JPH0552103A - Valve system of multiple cylinder internal combustion engine - Google Patents

Abstract

PURPOSE:To obtain high reliability in sealing property while reducing the number of parts, and simplifying construction. CONSTITUTION:Construction members 26I, 26E of one pressure chamber in the whole cylinders 12 or a plurality of cylinders 12, are fixed on a cylinder head 14. In the construction members 26I, 26E of the pressure chamber, passages 46I, 46E, 47I, 47E communicated with a plurality of air pressure chambers, are provided in common to respective air pressure chambers, and also bearing parts 30I, 30E are provided for supporting rotatably a cam shaft.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure chamber constituting member fixed to a cylinder head, in which a transmission piston, which is interlocked with and connected to a cam shaft common to all cylinders and fixed to an engine valve of each cylinder, is formed. The present invention relates to a valve operating system for a multi-cylinder internal combustion engine in which a pneumatic chamber capable of generating an air pressure for urging an engine valve in a valve closing direction is formed between a pressure chamber constituent member and a transmission piston in a slidable manner.

[0002]

2. Description of the Related Art Conventionally, such a valve operating device has been already known from, for example, Japanese Patent Laid-Open No. 2-283807.

[0003]

In such a valve operating system, the engine valve is biased in the valve closing direction by the air pressure of the air pressure chamber which the transmission piston faces, and the valve operating device using the valve spring has a valve spring which should be considered. The problem of resonance limit due to natural frequency is solved, and operation at higher rotation speed is possible. By the way, in the case of applying the valve operating system for a multi-cylinder internal combustion engine, conventionally,
One pressure chamber constituent member is fixed to the cylinder head for each cylinder, and the pipeline to be connected to each air pressure chamber is connected to each pressure chamber constituent member, resulting in a large number of parts. In addition to the complicated structure, there is a problem in reliability against leakage of air pressure. Moreover, the cam shaft is provided on the cylinder head between the pressure chamber constituent members and is rotatably supported by the cam holder, which also complicates the structure.

The present invention has been made in view of the above circumstances, and it is intended to reduce the number of parts and simplify the structure of the multi-cylinder internal combustion engine so as to obtain high reliability in sealing performance. An object is to provide a valve device.

[0005]

In order to achieve the above object, according to a first aspect of the present invention, one pressure chamber constituent member is fixed to a cylinder head for all cylinders or a plurality of cylinders. The pressure chamber constituent member is provided with a passage that should communicate with the plurality of air pressure chambers in common with each air pressure chamber, and a bearing portion that rotatably supports the cam shaft.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, a plurality of sleeves for respectively slidably fitting transmission pistons are inserted in the pressure chamber constituting member. It can be removed and fitted and fixed.

[0007]

Embodiments of the present invention will be described below with reference to the drawings.

1 to 10 show a first embodiment of the present invention. FIG. 1 is a schematic plan view of the device of the present invention, and FIG.
2 is a vertical cross-sectional view of the valve operating device taken along line 2-2 of FIG. 1, FIG. 3 is an enlarged vertical cross-sectional view of a main part of FIG. 2, FIG. 4 is a partial plan view of a pressure chamber constituent member, and FIG. Partial perspective view of the member, FIG. 6 is FIG.
6 is a longitudinal sectional view of the valve operating system taken along line 6-6 of FIG.
FIG. 8 is a side view of the internal combustion engine viewed from the direction of the arrow, and FIG.
8 is an enlarged sectional view taken along line 8, FIG. 9 is a diagram showing a pressure change of the pneumatic chamber with respect to the engine speed, and FIG. 10 is a sectional view showing a configuration of the volume chamber.

First, in FIGS. 1 and 2, four cylinders 12 are provided in parallel in a cylinder block 11 in this four-cylinder internal combustion engine, and a piston 13 slidably fitted in each cylinder 12 is provided. A combustion chamber 15 is formed between the cylinder head 14 and the cylinder head 14 coupled to the upper surface of the cylinder block 11. In addition, the cylinder head 14 has a pair of intake valve openings 16 facing the ceiling surface of each combustion chamber 15, and the intake port 1 that communicates with both intake valve openings 16 in common.
7 and a pair of exhaust valve openings 18 facing the ceiling surface of each combustion chamber 15.
And an exhaust port 19 commonly communicating with both exhaust valve openings 18 are provided corresponding to each cylinder 12, and a plurality of intake valves V _I as engine valves are used to open and close each intake valve opening 16. Is guided by a guide cylinder 20 provided in the upper and lower parts, and a plurality of exhaust valves V _E as engine valves are vertically movable by a guide cylinder 21 provided in the cylinder head 14 to open and close each exhaust valve port 18. Be guided.

Each intake valve V _I is provided with a valve body portion 22b capable of opening and closing the intake valve port 16 at the tip of a valve shaft portion 22a slidably inserted in the guide cylinder 20. , the exhaust valves V _E is the tip of the valve stem 23a which is slidably inserted into the guide cylinder 21, formed by openable valve body 23b is provided with an exhaust valve port 18.

Each intake valve V _I is opened and closed by an intake valve operating device 24 _I , and each exhaust valve V _E is exhausted by a valve operating device 24 _E.
Is driven to open and close by the intake side valve operating device 24.
_{Since the I} and the exhaust side valve operating device 24 _E have basically the same configuration, the intake side valve operating device 24 _{I will} be described below.
The configuration of the exhaust side valve operating device 24 _E will be described in detail with reference to the subscript “I”.
The main components corresponding to 4 _I are only shown in the figure with a subscript “E”.

In FIG. 3, the intake side valve operating device 24 _I is
A cam shaft 25 _I , which has an axis line orthogonal to the valve shaft portion 22 a of each intake valve V _I and is arranged in common in each cylinder 12,
Pressure chamber constituent member 26 _I fixed to the cylinder head 14
And a plurality of, for example, eight pistons 27 _I , which are interlocked and connected to the cam shaft 25 _I , are fixed to the respective intake valves V _I, and are slidably fitted to the pressure chamber constituting member 26 _I.

The cam shaft 25 _I is rotationally driven by a crank shaft (not shown) at a speed reduction ratio of 1/2, and is arranged above each intake valve V _I. Moreover, a cam 28 _I is integrally provided on the cam shaft 25 _I at a position corresponding to each intake valve V _I.

Referring to FIGS. 4 and 5 together, the pressure chamber constituting member 26 _I is common to all the cylinders 12, and is formed in a rectangular block shape elongated along the arrangement direction of each cylinder 12. And is connected to the cylinder head 14 at a position corresponding to each intake valve V _I. The pressure chamber constituent member 26 _I includes
A plurality of sliding holes 29 _I corresponding to each intake valve V _I , that is, one pair for each cylinder 12, are opened upward to open each intake valve V _I.
Are formed in the valve shaft 22a coaxially in _E, the rear end portion, that the upper end of the valve shaft portion 22 _a pressure chamber constituting member 2
Sliding hole 2 through the bottom of 6 _{I in} a fluid-tight and movable manner
It is rushed into 9 _I coaxially.

In the upper part of the pressure chamber constituting member 26 _I , a semicircular bearing part for supporting the lower half part of the cam shaft 25 _I is provided at a position corresponding to the mutually adjacent cylinders 12 and both end positions in the longitudinal direction. 30 _I are provided for each bearing unit 30.
In cooperation with _I being coupled to the upper portion of the pressure chamber component 26 _I at a position where the holder 31 _I for rotatably supporting the cam shaft 25 _I corresponds to the bearings 30 _I.

In each sliding hole 29 _I , a lifter 32 _I formed in a cylindrical shape with a bottom is slidably fitted with its closed end as an upper position. The outer surface of the closed end of the lifter 32 _I is brought into sliding contact with the cam 28 _I, and the inner surface of the closed end of the lifter 32 _I is brought into contact with the rear end or the upper end of the valve shaft portion 22a of the intake valve V _I. Therefore, the cam 28 _I and the valve shaft 22
The lifter 32 _I is provided between a and a.

A transmission pin is provided at a portion near the rear end of the valve shaft portion 22a.
Stone 27_IIs fixed. This transmission piston 27
_IIs an annular seal member 33 made of an elastic material._IThrough
Sliding hole 29_ISlidably fitted to the lifter
32_IA vacant space 34 between the closed end of the _IForming lifter 3
Two_IIs inserted in the transmission piston 27._ITosuri
Moving hole 29_IBetween the bottom of the air pressure chamber 35_IIs formed
It Moreover, the transmission piston 27_IIs a lifter 32_IClose side
It is formed in the shape of a double cylinder with a closed end and a
Seal member 33_ITransmission piston 27 above
_IThe outer surface of the lifter 32_IO-ring that slides on the inner surface of the
36_IIs fitted.

[0018] The rear end portion of the valve stem 22a, an annular engaging groove 37 _I is provided, the transmission piston through two split cotter 38 _I which engages the engaging groove 37 _I 27
_I is fixed to a portion near the rear end of the valve shaft portion 22a. Further, in order to prevent the air in the air pressure chamber 35 _I from leaking into the void chamber 34 _I from between the cotter 38 _I and the outer surface of the valve shaft portion 22a and the transmission piston 27 _I , the transmission piston 27 is located inside the cotter 38 _{I. A} valve shaft seal member 39 _I is attached to _I.

Sliding hole 29_IBottom of pressure chamber
Material 26_IAt the lower end of the air pressure chamber 35 _IA cylinder that rushes inside
Part 40_IAre provided coaxially, and the cylindrical portion 40_Iof
The upper end has a hole 41 for movably penetrating the valve shaft portion 22a.
_I42 which forms the inner edge of the _IOverhangs radially inward
Are integrated into one. The cylindrical portion 40_IGuide tube inside
The upper part of 20 is inserted, and this guide cylinder 20
And the collar portion 42_IAnnular so that it is sandwiched between
Seal member 43 for valve shaft_IIs the cylindrical portion 40_IInserted in
It

Each pressure chamber 3 has a pressure chamber constituent member 26 _I.
5 and the individual relief passage 44 _I leading to the lower part of the _I, and the individual supply passage 45 _I leading to the middle portion of the air pressure chambers 35 _I is provided corresponding to the respective pneumatic chambers 35 _I. Further, the pressure chamber constituent member 26 is provided on one side along the arrangement direction of each sliding hole 29 _I.
The _I, common relief passage 46 _I is closed at one end is provided in common to the pneumatic chamber 35 _I, the pressure chamber component 26 _I is on the other side along the arrangement direction of the slide hole 29 _I, at one end A closed common supply passage 47 _I is provided commonly to each pneumatic chamber 35 _I.

Referring also to FIG. 6, 2 for each cylinder 12
One of the slide hole 29 _I i.e. two separate relief passage 44 _I and the common relief passage 4 communicating with the two pneumatic chambers 35 _I
Relief valves 48 _I are installed between 6 _I and
Check valves 49 _I are provided between the two individual supply passages 45 _I and the common supply passage 47 _I , which communicate with the two sliding holes 29 _I, that is, the two air pressure chambers 35 _I for each cylinder 12.

Each relief valve 48 _I is a pressure chamber constituent member at a position corresponding to a common relief passage 36 _I between a pair of sliding holes 29 _I paired with each other for each cylinder 12, that is, a pair of pneumatic chambers 35 _I. 26 _I , each of which is provided in each of the two individual relief passages 44 _I and has a spherical valve body 53 _I biased by a spring 52 _I in a direction of closing the valve hole 51 _I commonly communicating with the two individual relief passages 44 _I. 36 _I made is accommodated in the valve chamber 54 _I which communicates with the spring 52 _I is mounted under compression between the screw member 55 _I and the valve body 53 _I screwed into the pressure chamber component 26 _I.

The relief valve 48 _I is connected to the air pressure chamber 35 _I.
When a predetermined amount or more of lubricating oil is accumulated in the air pressure chamber 35 _I and the pressure in the air pressure chamber 35 _I becomes higher than the pressure in the common relief passage 46 _{I by} a predetermined value or more, the valve is opened to release the air containing the lubricating oil from the air pressure chamber 35 _I. Is to be discharged.

Each check valve 49_IIs for each cylinder 12
A pair of sliding holes 29 which are paired with each other _II.e. a pair of sky
Pressure chamber 35_ICommon supply passage 47 between_ICorresponding to
Pressure chamber component 26 in position_IPlaced on each
And the common supply passage 47_IValve hole 55 leading to_IClosed
Spring 56_IValve element 57 biased by_IThere are two
Individual supply passage 45_ICommon valve chamber 58_IStored inside
The spring 56 _IIs a pressure chamber component 26_IScrewed into
Screw member 59_IAnd valve body 57_IIs reduced to between
It

The check valve 49 _I is connected to the air pressure chamber 35 _I.
When the internal air pressure becomes lower than the air pressure in the common supply passage 47 _I by a certain pressure or more, the valve is opened to supplement the pressurized air in the air pressure chamber 35 _I.

In FIGS. 7 and 8, the other end of the common relief passage 46 _I is opened so as to face the end wall 14a of the cylinder head 14 at one end side along the arrangement direction of the cylinders 12. A large diameter portion 61 _I is provided at the other end of the relief passage 46 _I. On the other hand, a mounting member 63 coaxial with the large-diameter portion 61 _I and having a fitting hole 62 of the same diameter is screwed to the end wall 14 a. The mounting member 63 and the end wall 14 a
An annular seal member 64 surrounding the screwing portion of the attachment member 63 to the end wall 14a is interposed between the and.

Both ends of a cylindrical joint 65 are fitted into the large diameter portion 61 _I and the fitting hole 62, and one end of the joint 65 is in contact with the inner surface of the large diameter portion 61 a at the outer surface thereof. A pair of annular seal members 66, 66 are fitted, and a pair of annular seal members 67, 67 that come into contact with the inner surface of the fitting hole 62 are fitted on the outer surface of the other end of the joint 65.

A cylindrical projection 63a coaxial with the fitting hole 62 is provided on the mounting member 63 so as to project outward through a step 64b, and a bolt 68 is screwed at the tip of the projection 63b. Are combined. Thus, the annular chamber 69 communicating with the inside of the joint 65
Ring-shaped connecting member 70 that forms the gap between the protrusion and the protrusion 63b.
Is sandwiched between the stepped portion 63b and the bolt 68, and an annular seal member 71 is provided between the stepped portion 63b and the connecting member 70.
And an annular seal member 72 is interposed between the bolt 68 and the connecting member 70. Moreover, the connecting member 70 is integrally provided with connecting pipe portions 70a and 70b which communicate with the annular chamber 69.

On the other hand, the common relief passage 46 _E in the exhaust-side valve operating device 24 _E is the same configuration as the common relief passage 46 _I in the intake-side valve operating device 24 _I, is attached to the end wall 14a of the cylinder head 14 A connection pipe portion 71 that is connected to the inside of the connection member 71 and is provided in the connection member 71.
a and the connecting pipe portion 70a of the connecting member 70 are connected to each other by the connecting pipe line 7
2 is connected. Further, the connecting pipe portion 7 of the connecting member 70
A conduit 73 is connected to 0b.

Further, the end of the common feed passage 47 _E in the common supply passage 47 _I and the exhaust-side valve operating device 24 _E in the intake-side valve operating device 24 _I is the common relief passage 4
6 _I and 46 _E have the same structure, and are connected to each other through a connecting pipe line 74 and are connected to a pipe line 75.

Referring again to FIG. 1, the conduit 73 connected to the common relief passages 46 _I and 46 _E is connected to the volume chamber 76, and a high precision solenoid valve 77 is connected to the lower portion of the volume chamber 76. Further, a pressure sensor 78 is attached to the volume chamber 76, and a detection value of the pressure sensor 78 is input to a control unit 79 which controls ON / OFF of the high precision solenoid valve 77.

The control unit 79 controls the opening of the solenoid valve 77 in response to the pressure in the volume chamber 76 becoming a predetermined value or more, as shown in FIG. 9 (a). When the engine speed becomes equal to or higher than the predetermined set speed N _ET , the solenoid valve 77 is operated as shown in FIG. 9 (b).
While closed (i.e. non executing the pressure control) it is intended to be, thereby, the pressure of the air pressure chamber 35 _I, 35 _E at the set rotational speed N _ET or more engine speed FIG 9 (c)
It will increase as shown in.

The common supply passage 47_I, 47_EConnected to
The line 75 is an accumulator via a regulator 81.
80 connected to the pipe 75, that is, the common supply passage.
47 _I, 47_EIs supplied with pressurized air at a constant pressure.
Becomes

In FIG. 10, a connection hole 8 communicating with the conduit 73 is provided on the side of the closed casing 83 forming the volume chamber 76.
4, a pressure sensor 78 is attached, and a solenoid valve 77 is connected via a filter 86 to a relief hole 85 opened at the bottom of the casing 83. Moreover, at the bottom of the casing 83, a partition plate 87, which is inclined upward toward the connection hole 84 so as to cover the relief hole 85, is fixed over the entire width of the casing 83.

With this structure, the lubricating oil contained in the air introduced into the volume chamber 76 from the conduit 73 through the connection hole 84 is located closer to the connection hole 84 than the partition plate 87 in the volume chamber 76. The oil can be stored, and the lubricating oil can be preferentially discharged from the relief hole 85 when the solenoid valve 77 is opened, so that wasteful discharge of air can be suppressed as much as possible.

Next, the operation of the first embodiment will be described. The intake side valve operating device 24 _I and the exhaust side valve operating device 24.
_{At E} , when the cam shafts 25 _I and 25 _E are rotationally driven by the crank shaft, the lifters 32 _I and 32 _E move to the cam 28
_{The I} , 28 _E are pushed downward in accordance with the sliding contact with the higher portion, whereby the valve shafts 22a, 23a of the intake valves V _I and the exhaust valves V _E are pushed downward, and the intake valves V _I , 28 _E are pushed downward. V _I
And each exhaust valve V _E is opened.

At this time, the transmission pistons 27 _I and 27 _E fixed to the rear end portions of the valve shafts 22a and 23a are also driven downward while contracting the volumes of the pneumatic chambers 35 _I and 35 _E , Air pressure is generated in the air pressure chambers 35 _I and 35 _E. As a result, the intake valve V _I and the exhaust valve V _E are biased upward by the air pressure, that is, in the valve closing direction, and the cams 28 _I and 28 _E resist the biasing force of the air pressure in the valve closing direction. The V _I and the exhaust valve V _E are driven to open.

According to the structure in which the intake valve V _I and the exhaust valve V _E are biased in the valve closing direction by the air pressure as described above, the resonance limit due to the natural frequency is higher than that of the valve spring biased valve closing bias. Since it is not necessary to consider the above, it becomes possible to operate the engine at a higher rotation speed.

According to such valve operating devices 24 _I and 24 _E ,
Pressure chamber constituent members 26 _I , 26 _E are integrally provided corresponding to all the cylinders 12, and common relief passages 46 _I , 46 _E and common supply passage 47 _I common to the air pressure chambers 35 _I , 35 _E are provided. Since 47 _E is provided in the pressure chamber constituent members 26 _I and 26 _E , the valve operating devices 24 _I and 24 _E can be made compact and the number of parts can be reduced, and the common relief passage It is possible to improve the reliability against leakage of air pressure by reducing the portion of the connection to the 46 _I and 46 _E and the common supply passages 47 _I and 47 _{E in} which the sealing property is to be considered.

Moreover, the end portions of the common relief passages 46 _I and 46 _E and the common supply passages 47 _I and 47 _E are fitted into the pressure chamber constituting members 26 _I and 26 _E via the seal members 66 and 66, and the cylinder head. Since it is connected to the conduits 73, 75 via a cylindrical joint 61 _I or the like fitted to the end wall 14a of the pressure roller 14 via the seal members 67, 67, it is a pressure chamber constituent member for the cylinder head 14. Two
By absorbing the mounting error of 6 _I and 26 _E , it becomes possible to relieve and supply pressurized air.

Bearing portions 30 _I , 30 for supporting the cam shafts 25 _I , 25 _E on the pressure chamber constituent members 26 _I , 26 _E.
By providing _E , it is possible to maintain high rigidity against the thrust force due to the rotation of the cam shafts 25 _I and 25 _E , to increase the engine speed and increase the valve lift.

Further, the individual relief passages 44 _I and 44 _{E, which} are connected to the common relief passages 46 _I and 46 _E via the relief valves 48 _I and 48 _E , are opened below the air pressure chambers 35 _I and 35 _E. , pneumatic chamber 35 _I, 35 accumulates a predetermined amount or more of lubricant oil in the air pressure chamber 35 _I, 35 in _E
When the pressure in _E becomes equal to or higher than the preset maximum pressure, priority is given to discharging accumulated lubricating oil to avoid wasteful discharge of air, and prevent wasteful consumption of compressed air from the accumulator 80. You can

Moreover, the common relief passage 4 is connected to the air pressure chambers 35 _I and 35 _E via the relief valves 48 _I and 48 _E.
Since 6 _I and 46 _E are connected to the volume chamber 76 and the internal pressure of the volume chamber 76 is controlled by the high precision solenoid valve 77,
With changes in air pressure in the pneumatic chamber 35 _I, 35 _E at a certain cylinder is prevented from adversely affecting the air pressure chamber 35 _I, 35 _E in the other cylinders, each air pressure chamber 35
It is possible to accurately control the pressure in _I and 35 _E.

Further, as shown in FIG. 9, the control unit 79 is operated when the engine speed exceeds the set speed N _ET.
Since the control of the solenoid valve 77 by the engine is stopped, when the engine speed is equal to or higher than the set speed N _ET , the air pressure chamber 35 _I ,
The air pressure of 35 _E can be increased, and the spring load according to the engine speed can be obtained.

FIG. 11 shows a second embodiment of the present invention, in which the engine speed shown in FIG. 11 (a) is the set speed N _ET.
As shown in FIG. 11B, the pressure of the pressurized air supplied to the common supply passages 47 _I and 47 _E in response to
It is controlled in stages (or multiple stages). By doing so, the pressure inside the air pressure chambers 35 _I and 35 _E changes as shown in FIG. 11 (c), and when the engine speed fluctuates greatly, the pressure inside the air pressure chambers 35 _I and 35 _E becomes more responsive. It is possible to control in two stages (or multiple stages) with good performance.

As a third embodiment of the present invention, in response to the internal pressure of the accumulator 80 becoming equal to or lower than the set pressure P _T as shown in FIG. 12 (a), the common supply passage as shown in FIG. 12 (b). The pressure of the pressurized air supplied to 47 _I and 47 _E may be lowered, which can contribute to the reduction of the air consumption.

FIG. 13 shows a fourth embodiment of the present invention. The volume chamber 76 is connected to the pipe line 75 via a high precision solenoid valve 77 and a check valve 88, and the volume chamber 76 is provided with a regulator 81. The accumulator 80 is connected via the.

According to the fourth embodiment, the solenoid valve 7
The high-pressure air controlled by 6 and discharged from the volume chamber 76 is supplied to the common supply passages 47 _I and 47 _E, and the amount of air supplied from the accumulator 80 can be greatly reduced.

FIG. 14 shows a fifth embodiment of the present invention. The volume chamber 76 is connected to the volume chamber 89 via a high precision solenoid valve 77 and a check valve 88, and the volume chamber 8 is connected to the volume chamber 89.
9 is connected to the pipe line 75 and accumulator 81
Is connected to the accumulator 80.

According to the fifth embodiment, the air consumption can be reduced by circulating the relief air to the supply side as in the fourth embodiment, and the common supply passage can be controlled during the control by the solenoid valve 76. The fluctuation of the air pressure generated in 47 _I and 47 _E can be suppressed by the volume chamber 89.

By the way, when the lubricating oil-containing air discharged from the air pressure chambers 35 _I and 35 _E is circulated to the supply side as in the fourth and fifth embodiments, as in the sixth embodiment shown in FIG. , The lubricating oil in the circulating air, the pneumatic chamber 3
It can also be used to prevent the seizure of the sliding contact surfaces of the lifters 32 _I and 32 _E and the cams 28 _I and 28 _{E as} the temperature rises to 5 _I and 35 _E.

In FIG. 15, the pressure chamber constituent members 26 _I ,
26 The _E, ejection hole 90 _I was communicated at one end to a common supply passage 47 _I, 47 _E, 90 _E are each slide hole 29 _I, 29 _E
Corresponding to each of the ejection holes 90 _I ,
The other end of 90 _E is opened when the lifters 32 _I and 32 _E pushed by the cams 28 _I and 28 _E descend to the lowermost position as shown by the chain line, and the upper portions of the sliding holes 29 _I and 29 _E are covered. To be opened.

According to the sixth embodiment, each intake valve V_IOh
And each exhaust valve V_EOnly when the valve is open
Lubricant oil spouts 90_I, 90_EFrom lifter 32_I，
32 _EAnd cam 28_I, 28_EGushing toward the sliding contact surface
Common supply passage 47_I, 47_EPressure inside
The seizure of the sliding contact surface is minimized while minimizing the force drop.
Can be prevented.

FIG. 16 shows a seventh embodiment of the present invention.
Yes, pressure chamber component 26_I, 26 _EThe transmission piste
27_I, 27_EAnd lifter 32_I, 32_EThat
Cylindrical sleeve 91 that is slidably fitted_I, 91_E
Is fitted and fixed so that it can be inserted and removed, for example, by light press-fitting.
It

According to this seventh embodiment, the transmission piston 2
7 _I , 27 _E and the lifters 32 _I , 32 _E can be dealt with by replacing the sleeves 91 _I , 91 _E with abrasion due to friction with them.

FIG. 17 shows an eighth embodiment of the present invention.
Yes, each pneumatic chamber 35_I, 35_EInside the pressure chamber component
Material 26_I, 26_EAnd transmission piston 27_I, 27_Ewhile
Spring 92 contracted to_I, 92_EAre stored respectively
It Each spring 92_I, 92 _ESpring load is pneumatic
Room 35_I, 35_ETransmission piston 27 due to pressure drop inside
_I, 27_ESet to a value that is extremely weak enough to prevent the
Is determined.

According to the eighth embodiment, even if the internal pressure of the air pressure chambers 35 _I and 35 _E drops when the engine is left for a long period of time, the transmission pistons 27 _I and 27 _E are prevented from falling, and Thus, the cotter 38 _I can be prevented from coming off, and the intake valve V _I and the exhaust valve V _E can be prevented from falling off. Further, at the time of low rotation such as when the engine is started, high air pressure is not required, and by utilizing the spring force of the springs 92 _I and 92 _E , it is possible to operate with reduced friction loss.

FIG. 18 shows a ninth embodiment of the present invention in which the common relief passages 46 _I and 46 _E are connected to the individual relief passages 44 _I and 44 _E through orifices 93 _I and 93 _E , respectively. The common supply passages 47 _I and 47 _E are connected to the individual supply passages 45 _I and 45 _E via orifices 94 _I and 94 _E.

According to the ninth embodiment, it is possible to control the air pressure of each of the air pressure chambers 35 _I and 35 _E with respect to the engine speed with good followability and accuracy.

In the above embodiment, the pressure chamber constituent member 2
Although 6 _I and 26 _E are integrally formed over all cylinders, the pressure chamber constituent members may be integrally formed over a plurality of cylinders among the multiple cylinders.

[0061]

As described above, according to the first feature of the present invention, one pressure chamber constituent member is fixed to the cylinder head for all cylinders or a plurality of cylinders, and the pressure chamber constituent member is Since a passage that should connect to multiple air pressure chambers is provided in common to each air pressure chamber and a bearing that rotatably supports the cam shaft is provided, the number of parts can be reduced and the structure of the valve train can be made compact. In addition, it is possible to obtain high reliability in terms of sealing performance, and it is possible to improve the rigidity of the cam shaft support portion.

According to the second feature of the present invention, in addition to the configuration of the first feature, a plurality of sleeves for respectively slidably fitting the transmission pistons are inserted in the pressure chamber constituting member. Since it can be removed and fitted and fixed, wear due to friction with the transmission piston can be dealt with by replacing the sleeve.

[Brief description of drawings]

FIG. 1 is a schematic plan view of a device of the present invention according to a first embodiment.

FIG. 2 is a vertical cross-sectional view of the valve operating system taken along line 2-2 of FIG.

FIG. 3 is an enlarged vertical sectional view of a main part of FIG.

FIG. 4 is a partial plan view of a pressure chamber constituent member.

FIG. 5 is a partial perspective view of a pressure chamber constituent member.

FIG. 6 is a vertical cross-sectional view of the valve operating system taken along line 6-6 of FIG.

FIG. 7 is a side view of the internal combustion engine viewed from the direction of arrow 7 in FIG.

8 is an enlarged sectional view taken along line 8-8 of FIG.

FIG. 9 is a diagram showing a pressure change of an air pressure chamber with respect to an engine speed.

FIG. 10 is a cross-sectional view showing a configuration of a volume chamber.

FIG. 11 is a diagram showing a pressure change of an air pressure chamber with respect to an engine speed of a second embodiment.

FIG. 12 is a diagram showing a change in supply pressure with respect to an accumulator internal pressure in the third embodiment.

FIG. 13 is a schematic plan view corresponding to FIG. 1 of the fourth embodiment.

FIG. 14 is a schematic plan view corresponding to FIG. 1 of the fifth embodiment.

FIG. 15 is a vertical sectional view corresponding to FIG. 2 of the sixth embodiment.

FIG. 16 is a schematic plan view corresponding to FIG. 1 of the seventh embodiment.

FIG. 17 is a vertical sectional view corresponding to FIG. 2 of the eighth embodiment.

FIG. 18 is a schematic plan view corresponding to FIG. 1 of the ninth embodiment.

[Explanation of symbols]

12 cylinders 14 cylinder head 24 _I intake side valve operating device 24 _E exhaust side valve operating device 25 _I , 25 _E camshaft 26 _I , 26 _E pressure chamber constituent member 27 _I , 27 _E transmission piston 30 _I , 30 _E bearing portion 35 _I, 35 _E pneumatic chamber 46 _I, 46 _E passages 47 _I, 47 _E passages 91 _I, 91 an exhaust valve of the intake valve V _E engine valve as _E sleeve V _I engine valve

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[Procedure amendment]

[Submission date] May 13, 1992

[Procedure Amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0012

[Correction method] Change

[Correction content]

In FIG. 3, the intake side valve operating device 24 _I is
A cam shaft 25 _I , which has an axis line orthogonal to the valve shaft portion 22 a of each intake valve V _I and is arranged in common in each cylinder 12,
Pressure chamber constituent member 26 _I fixed to the cylinder head 14
And a plurality of, for example, eight transmission pistons 27 that are interlocked with and connected to the cam shaft 25 _I , are fixed to the intake valves V _I, and are slidably fitted to the pressure chamber constituent member 26 _{I.
With I} and.

[Procedure Amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0014

[Correction method] Change

[Correction content]

Referring to FIGS. 4 and 5 together, the pressure chamber constituting member 26 _I is common to all the cylinders 12, and is formed in a rectangular block shape elongated along the arrangement direction of each cylinder 12. And is connected to the cylinder head 14 at a position corresponding to each intake valve V _I. The pressure chamber constituent member 26 _I includes
A plurality of sliding holes 29 _I corresponding to each intake valve V _I , that is, one pair for each cylinder 12, are opened upward to open each intake valve V _I.
Are formed in the valve shaft 22a coaxially in _E, the rear end portion, that the upper end of the valve shaft portion 22 a pressure chamber constituting member 2
Sliding hole 2 through the bottom of 6 _{I in} a fluid-tight and movable manner
It is rushed into 9 _I coaxially.

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0028

[Correction method] Change

[Correction content]

[0028] the mounting member 63 includes a cylindrical protrusion 63a is fitting hole 62 coaxial with and projecting outwardly through a step portion 6 3 b, the tip of the projecting portion 63 a bolt 68 is screwed. Thus, the annular chamber 69 communicating with the inside of the joint 65
Ring-shaped connecting member 70 that forms a gap between the protrusion and the protrusion 63a.
Is sandwiched between the stepped portion 63b and the bolt 68, and an annular seal member 98 is provided between the stepped portion 63b and the connecting member 70.
And an annular seal member 99 is interposed between the bolt 68 and the connecting member 70. Moreover, the connecting member 70 is integrally provided with connecting pipe portions 70a and 70b which communicate with the annular chamber 69.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0049

[Correction method] Change

[Correction content]

FIG. 14 shows a fifth embodiment of the present invention. The volume chamber 76 is connected to the volume chamber 89 via a high precision solenoid valve 77 and a check valve 88, and the volume chamber 8 is connected to the volume chamber 89.
9 is connected to the pipe line 75 and is connected to the accumulator 80 via the regulator 81.

[Procedure Amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0052

[Correction method] Change

[Correction content]

In FIG. 15, the pressure chamber constituent members 26 _I ,
26 The _E, one end a common feed passage 47 _I, 47 ejection holes were communicated with the _E 90 _I, 90 _E are each slide holes 29 _I, 29 _E
Corresponding to each of the ejection holes 90 _I ,
The other end of 90 _E is opened when the lifters 32 _I and 32 _E pushed by the cams 28 _I and 28 _E descend to the lowermost position as shown by the chain line, and the upper portions of the sliding holes 29 _I and 29 _E are covered. To be opened.

[Procedure Amendment 6]

[Document name to be corrected] Drawing

[Correction target item name] Figure 8

[Correction method] Change

[Correction content]

[Figure 8]

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁵ Identification code Internal reference number FI Technical display location F01L 3/10 Z 7114-3G 3/12 D 7114-3G 3/14 G 7114-3G Z 7114- 3G (72) Inventor Iwao Kakuda 1-4-1 Chuo, Wako-shi, Saitama, Ltd. Honda R & D Co., Ltd.

Claims (2)

[Claims] 1. A cam shaft (2) common to all cylinders (12).
5_I, 25_E) And each cylinder (1
2) Engine valve (V_I, V_E) Transmission fixed to each
Piston (27_I, 27_E) Is the cylinder head (1
4) fixed to the pressure chamber constituting member (26_I, 26_E) To
Slidingly fitted, the pressure chamber component (26 _I, 2
6_E) And transmission piston (27_I, 27_EBetween),
Engine valve (V_I, V _E) To generate air pressure that biases
Producable air pressure chamber (35_I, 35_E) Is formed
In a valve operating system for a cylinder internal combustion engine, all cylinders (12) or
One pressure chamber constituent member (2
6_I, 26_E) Is fixed to the cylinder head (14),
The pressure chamber constituent member (26_I, 26_E) Has more than one air
Pressure chamber (35_I, 35_E) Passage (46_I, 4
6_E, 47_I, 47_E) Is each pneumatic chamber (35_I, 3
5_E) And the camshaft (25_I，
25_E) Rotatably bearings (30_I, 3
0_E) Is provided in a multi-cylinder internal combustion engine
Valve drive. 2. A plurality of sleeves (91 _I , 91 _E ) into which the transmission pistons (27 _I , 27 _E ) are slidably fitted are inserted in the pressure chamber constituent members (26 _I , 26 _E ). The valve operating system for a multi-cylinder internal combustion engine according to claim 1, wherein the valve operating system is fitted and fixed so as to be detachable.