JPH07279699A - Variable cylinder controller of odd number multi-cylinder engine - Google Patents

Abstract

PURPOSE:To enable operation stopping without necessitating any complicate control, so as to prevent generation of irregular engine vibration by connecting intake cutoff valves provided in respective intake passages to each other by a connecting member by phase, and driving the connecting member through a process of synchronizing it with the rotation of an engine by means of a driving means. CONSTITUTION:In a five-cylinder engine, intake cutoff valves 4 provided in intake pipes of respective cylinders are attached to a common shaft 4a providing the phase difference of 108 deg. between the cylinders, and they are driven through a toothed belt 6 wound around pulleys 4b, 5b by the reduction ratio of 1 to 4 in relation to a cam shaft 5a. Thereby, when a first cylinder is in a start point of the intake stroke, the intake cutout valve 4 of a second cylinder to be next ignited is made in the position of 1.25+108=119.25 deg. in relation to an axis of an intake pipe 3 counterclock and then rotated clockwise by 22.5 deg. during the intake stroke of the second cylinder, however, the peripheral end of the intake cutoff valve is approached to the wall part of the intake pipe 3, so as to shut the intake passage 3a, and the second cylinder is taken as the stop cylinder.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to variable cylinder control of an odd multi-cylinder engine.

[0002]

2. Description of the Related Art Variable cylinder control is being developed even in odd-numbered multi-cylinder engines. However, in variable cylinder control of odd-numbered multi-cylinder engines, when certain cylinders are deactivated, explosion intervals become uneven and irregular. There is a problem that engine vibration occurs. Therefore, a method of performing variable cylinder control on an odd-numbered multi-cylinder engine without changing the stationary cylinders in order and changing the order in order to make the explosion intervals even and without causing the above irregular engine vibration is proposed. For example, there is one disclosed in Japanese Patent Laid-Open No. 5-195830. According to the publication, a variable cylinder control mechanism is incorporated in the valve actuation mechanism of each cylinder, and electronically controlled hydraulic pressure is supplied to the variable cylinder control mechanism incorporated in the valve actuation mechanism.

[0003]

However, in the method proposed in the above publication, it is necessary to incorporate a variable cylinder control mechanism into the valve actuation mechanism of each cylinder, and the conventional valve actuation mechanism cannot be used as it is. In addition, there is a problem that the control becomes complicated because it is necessary to control the hydraulic pressure supplied to the variable cylinder control mechanism for each cylinder. In view of the above problems, an object of the present invention is to provide a variable cylinder control device for an odd-numbered multi-cylinder engine that does not require complicated control and repeats operation pauses at equal intervals to prevent irregular engine vibration. .

[0004]

According to the first aspect of the present invention, the intake cutoff valve disposed in the intake passage of each cylinder, the connecting member connecting the intake cutoff valves, and the connecting member are provided. The connecting member connects the intake cutoff valve in the intake passage of each cylinder at the same phase difference as the phase difference of the operation cycle, and the connecting member connects the intake cutoff valve with the intake stroke each time the intake stroke arrives. The shut-off valve drives the connecting member in synchronization with the engine rotation so as to alternately take a position that shuts off the intake passage and a position that does not shut off the intake passage. A variable cylinder controller for an odd multi-cylinder engine characterized by repeating is provided. According to a second aspect of the present invention, the storage section for storing the intake cutoff valve is provided so as not to block the intake passage, and the intake cutoff valve is stored in the storage section during all cylinder operation. A variable cylinder controller for an odd multi-cylinder engine is provided. According to claim 3, further, a bypass passage is provided for bypassing the intake passage provided with the intake cutoff valve, and intake is performed through the bypass passage during all cylinder operation. A variable cylinder controller for the described odd multi-cylinder engine is provided. . According to claim 4, further, the phase varying means capable of changing the phase of the intake cutoff valve is provided so that the intake cutoff valve always cuts off the intake passage every time the intake stroke comes during all cylinder operation. The variable cylinder control device for an odd number multi-cylinder engine according to claim 1, wherein the phase of the intake cutoff valve is shifted to a position where there is no position.

[0005]

According to the present invention, the intake cutoff valves provided in the respective intake passages are connected in phase by the connecting members, and the connecting members are driven in synchronization with the rotation of the engine by the drive means, so that the individual intake cutoff valves are connected. The intake cutoff valves of all the cylinders are controlled by one control means without independently controlling each of the above. In the second aspect, the intake cutoff valve is stored while being shifted from the intake passage during the operation of all cylinders, so that the all-cylinder operation is performed without the cylinder whose intake passage is blocked by the intake cutoff valve. In the third aspect, when all cylinders are in operation, air is taken in through the bypass passage that bypasses the intake passage provided with the intake cutoff valve, so that all cylinder operation is performed without the cylinder in which the intake passage is blocked by the intake cutoff valve. Further, according to the present invention, when all the cylinders are operated, the intake cutoff valve is inhaled in a state in which the phase is shifted so that the intake cutoff valve always comes to a position where it is opened in the intake stroke, so that the intake passage is blocked by the intake cutoff valve. Cylinder operation is performed.

[0006]

Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 shows a first embodiment of the present invention applied to a 5-cylinder engine.
It is the figure which showed the structure of the Example typically. In FIG. 1, reference numeral 1 is an air cleaner, 2 is a surge tank, and an intake throttle valve 1a for controlling the intake air amount is disposed between them. It may be provided on the tube. An intake pipe 3 connects the surge tank 2 and the intake port of each cylinder. An intake passage 3a is formed in the intake pipe 3. Reference numeral 4 denotes an intake cutoff valve provided in each intake pipe of each cylinder, which is attached to a common shaft 4a with a phase difference between the cylinders.
The shaft 4a is provided with a toothed belt 6 via a pulley 4b mounted on the shaft 4a and a pulley 5b mounted on the cam shaft 5a.
Is driven at a reduction ratio of 1/4 with respect to the cam shaft 5a. Since the camshaft 5a is driven at a reduction ratio of 1/2 with respect to the crankshaft 7a, the shaft 4a of the intake cutoff valve is driven at a reduction ratio of 1/8 with respect to the crankshaft 7a. . The common shaft 4a to which the intake cutoff valve 4 of each cylinder is attached is the connecting means in claim 1, and the cam shaft 5a, the pulley 4b, the pulley 5b and the toothed belt 6 for interlocking them are driven. It plays the role of means. Instead of decelerating through the camshaft as in the first embodiment, it is also possible to decelerate directly from the crankshaft with a deceleration ratio of 1/8.

FIG. 2 is a schematic drawing showing the state of the intake cutoff valve for each cylinder attached to the shaft 4a, and FIG. 3 shows the phase difference between the cylinders. Ignition is performed every 144 degrees CA (crank angle) in all cylinders operation of this 5-cylinder engine, and the order is # 1- # 2- # 4-.
It is # 5- # 3 cylinder. The phase difference of the intake cutoff valves between the cylinders in the ignition order is 108 degrees. That is, the phase difference between the intake cutoff valve of the # 1 cylinder and the intake cutoff valve of the # 2 cylinder is 108 degrees, and the phase difference between the intake cutoff valve of the # 2 cylinder and the intake cutoff valve of the # 4 cylinder is 108 degrees. The phase difference between the intake cutoff valve of the # 4 cylinder and the intake cutoff valve of the # 5 cylinder is 108
The phase difference between the intake cutoff valve of the # 5 cylinder and the intake cutoff valve of the # 3 cylinder is 108 degrees, and the phase difference between the intake cutoff valve of the # 3 cylinder and the intake cutoff valve of the # 1 cylinder is 108 degrees.

FIG. 4 shows the intake cutoff valve 4 with respect to the crank angle.
It is a figure which shows the position of. AO ₁ is the position of the intake cutoff valve 4 when the piston of the # 1 cylinder is at the start point of the intake stroke, that is, at the intake TDC, and its operation is not stopped, and is on the central axis of the intake pipe 3. On the other hand, the position is 11.25 degrees counterclockwise, and AO ₂ indicates that the piston of the # 1 cylinder is the end point of the intake stroke, that is, the intake BDC.
That is, the position of the intake cutoff valve 4 when the operation is not stopped, and the position is 11.25 degrees clockwise with respect to the central axis of the intake pipe 3. Therefore, when the piston moves from the intake air TDC to the intake air BDC and the crankshaft 7a rotates 180 degrees, the intake air cutoff valve 4 becomes A.
From point O _{1 to} point AO ₂ , the rotation will be 11.25 ° + 11.25 ° = 22.50 °. This is because the shaft 4a of the intake cutoff valve is rotated at a speed reduction ratio of 1/8 with respect to the crankshaft 7a.

On the other hand, AC ₁ indicates the position of the intake cutoff valve 4 when the piston of the # 1 cylinder is at the start point of the intake stroke, that is, at the intake TDC and the operation is stopped. 78. clockwise with respect to the central axis of 3.
The position is 75 degrees, and AC ₂ indicates the position of the intake cutoff valve 4 when the piston of a certain cylinder is at the end point of the intake stroke, that is, at the intake BDC and its operation is stopped. 10 clockwise with respect to the central axis of tube 3.
The position is 1.25 degrees.

From the AO ₁ point, the intake cutoff valve 4
By the time it moves to point C _1, it rotates 11.25 + 78.75 = 90 degrees, but during this period, the crankshaft rotates 90 degrees × 8 = 720 degrees. This is a period in which four strokes of intake, compression, explosion and exhaust are completed in a four-cycle engine,
Therefore, in the intake stroke that follows the cylinder after the intake stroke in which the operation is not stopped, the intake cutoff valve 4 comes to the position where the intake passage 3a is closed and stops the operation.
Further, in the next intake stroke, the intake cutoff valve 4 is at the position where the intake passage 3a is open, so the operation is not stopped. Thus, in this embodiment, the intake stroke is 1 for each cylinder.
It is deactivated every other time.

Next, FIG. 5 is a diagram for explaining the sequence of deactivating the intake cutoff valve 4 between the cylinders. # 1 cylinder is AO ₁
When it is at the point, the intake cutoff valve of the # 2 cylinder that ignites next,
As described above, since there is a phase difference of 108 degrees, counterclockwise rotation with respect to the axis of the intake pipe 3 is 11.25 + 108 = 1.
It is located at 19.25 degrees and is designated B (AO ₁ ). On the other hand, the intake stroke of the second cylinder for the next ignition is # 1.
Crankshaft 7a only 144 degrees CA after the start of the intake stroke of the cylinder
Is started at the time of rotation, because in the five-cylinder engine of the present embodiment, as described above, ignition is performed five times during 720 degrees CA, that is, ignition is performed once every 144 degrees CA. This is because each process is performed once every 144 degrees CA.

When the crankshaft 7a rotates by an angle of 144 degrees CA, the intake cutoff valve 4 rotates by 144/8 = 18 degrees. Therefore, at the start of the intake stroke of the # 2 cylinder, the intake cutoff valve of the # 2 cylinder is rotated counterclockwise 119.25 with respect to the axis of the intake pipe 3 as indicated by BC _1.
It is located at -18 = 101.25 degrees. This is counterclockwise with respect to the axis perpendicular to the axis of the intake pipe 11.
It means that it is located at a position of 25 (= 101.25-90) degrees. The intake cutoff valve of the # 2 cylinder thereafter rotates clockwise by 22.5 degrees during the intake stroke of the second cylinder, and the peripheral end of the intake cutoff valve 4 is the wall of the intake pipe 3 during that time. Is closest to the cylinder, the intake passage 3a is cut off, and the cylinder # 2 is a deactivated cylinder that does not operate.

FIG. 6 is a diagram showing the movement of the intake cutoff valve 4 of each cylinder at every 144 ° CA with reference to the intake TDC at which the # 1 cylinder is about to start intake.
-# 2- # 4- # 5- # 3 It is shown that the intake strokes are performed in the same order as the cylinders, and the intake strokes are paused every other stroke. As shown in FIG. 6, since the intake cutoff valve 4 is closed every other cylinder during the reduced cylinder operation, the explosion intervals become uniform,
Irregular engine vibration during reduced cylinder operation is reduced. In addition, the intake passage 3a is mechanically driven by the rotation of the crankshaft 7a.
Since it is opened and closed, complicated control is not required.

If the intake cutoff valve as described above is provided as it is, the cylinders in the intake stroke are always deactivated every other time, so that all cylinders cannot be operated as they are. Therefore, it is possible to operate all cylinders by combining the following methods. FIG. 7 schematically shows the structure of the second embodiment of the present invention, in which the intake cutoff valve as in the first embodiment is provided inside the intake pipe 3 and the intake cutoff valve is provided. A storage part is provided, and the intake cutoff valve is shifted and stored in the storage part during all cylinder operation,
The intake passage of any cylinder is designed so as not to be completely throttled. In the figure, reference numeral 8 denotes an intake cutoff valve storage portion, a spring 9 for constantly urging the shaft 4a to an intake throttle operating position is provided at one end of the shaft 4a, and a hydraulic operation is provided at the other end. When the chamber 10 is provided and hydraulic pressure is supplied, the shaft 4a is moved against the urging force of the spring 9 and the intake cutoff valve is moved to the retracted position. Therefore, during the operation of all cylinders, the hydraulic pressure is supplied to the hydraulic working chamber 10, whereby the intake cutoff valve 4 is stored in the intake cutoff valve storage portion 8 and a sufficient intake air amount (intake passage area) is secured. .

FIG. 8 schematically shows the structure of the third embodiment of the present invention, in which the intake cutoff valve as in the first embodiment is provided inside the intake pipe 3, and Bypass passage 11 for all cylinder operation that bypasses the intake pipe 3 for each cylinder
Is provided at the branch portion of the bypass passage 11 and the intake pipe 3 is provided with a switching valve 12 that shuts off the bypass passage 11 during reduced cylinder operation and shuts off the intake pipe 3 during all cylinder operation.
The switching valve 12 is controlled by an electronic control unit (not shown), and the bypass passage 11 is fully opened during operation of all cylinders. Therefore, since the intake air is supplied only from the bypass passage 11 during the operation of all cylinders, the intake cutoff valve 4 does not have a passage resistance, and a sufficient intake air amount (intake passage area) is secured.

FIG. 9 schematically shows the structure of the fourth embodiment of the present invention.
In addition to providing the intake cutoff valve as in the above embodiment, the phase of the axis of the intake cutoff valve is made variable so that the intake cutoff valve in the intake stroke is not always fully closed during all cylinder operation. . In the figure, 13 is a hydraulic working chamber, in which a helical spline 14 as a phase varying means is incorporated, and when hydraulic pressure is supplied, the phase with respect to the pulley 4b changes. In this embodiment, the phase is changed by 45 degrees when hydraulic pressure is supplied during all cylinder operation.

FIG. 10 shows the position of the intake cutoff valve when the phase is shifted by 45 degrees with respect to the partial cylinder operation during the full cylinder operation as described above. As shown in FIG. During the intake stroke period that appears every 90 degrees, a gap is maintained between the intake cutoff valve and the intake pipe wall, so that the idle cylinder in which the intake passage is closed disappears and all cylinder operation is performed. As described above, the fourth embodiment does not require the storage portion for the intake cutoff valve as in the second embodiment or the bypass passage as in the third embodiment, so that the engine can be operated in all cylinders without increasing the size of the engine. It is possible to switch the reduced cylinder operation.

[0018]

Since the present invention is constructed and operates as described above, according to the first aspect of the present invention, all the cylinders can be operated by one driving means without independently controlling each intake cutoff valve. Since the intake cutoff valve is controlled, complicated control is not required. Further, according to the second, third, and fourth aspects, all cylinder operation can be performed without cylinders in which the intake passage is blocked by the intake cutoff valve during all cylinder operation. Further, in claim 4, since the storage part of the intake cutoff valve as in claim 2 and the bypass passage as in claim 3 are not required, it is possible to switch between all cylinder operation and reduced cylinder operation without increasing the size of the engine. Is.

[Brief description of drawings]

FIG. 1 is a schematic view of the structure of the first embodiment of the present invention.

FIG. 2 is a diagram in which only an intake cutoff valve is drawn out.

FIG. 3 is a diagram showing a phase difference between intake cutoff valves for each cylinder.

FIG. 4 is a diagram showing a position of an intake cutoff valve in an intake stroke of a # 1 cylinder.

FIG. 5 is a diagram showing a positional relationship between an intake cutoff valve for a # 1 cylinder and an intake cutoff valve for a # 2 cylinder.

FIG. 6 is a diagram showing the movement of the intake cutoff valve of each cylinder for every 144 degrees.

FIG. 7 is a diagram schematically showing the structure of a second embodiment of the present invention.

FIG. 8 is a diagram schematically showing the structure of the third embodiment of the present invention.

FIG. 9 is a diagram schematically showing the structure of the fourth embodiment of the present invention.

FIG. 10 is a diagram showing the position of the intake cutoff valve in the intake stroke when the phase is shifted by 45 degrees in the fourth embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Air cleaner 1a ... Intake throttle valve 2 ... Surge tank 3 ... Intake pipe 4 ... Intake shutoff valve 4a ... Intake shutoff valve shaft 4b ... Pulley 5a ... Cam shaft 5b ... Pulley 6 ... Toothed belt 7a ... Crankshaft 8 ... Storage part 9 ... Spring 10 ... Hydraulic operating chamber 11 ... Bypass passage 12 ... Switching valve 13 ... Hydraulic operating chamber 14 ... Helical spline # 1 ... No. 1 cylinder # 2 ... No. 2 cylinder # 3 ... No. 3 cylinder # 4 ... No. 4 cylinder # 5th cylinder # 5

Claims (4)

[Claims] 1. An intake cutoff valve disposed in an intake passage of each cylinder, a connecting member for connecting the intake cutoff valves, and a drive unit for driving the connecting member, wherein the connecting member includes The intake cutoff valve in the intake passage of the cylinder is connected with the same phase difference as the phase difference of the operation cycle, and the intake cutoff valve closes the intake passage each time the drive means reaches the intake stroke, and the intake passage Variable cylinder control for odd-numbered multi-cylinder engines characterized by repeating operation pauses at even intervals during reduced-cylinder operation by driving the connecting members in synchronization with the engine rotation so that the positions that do not shut off are alternated. apparatus. 2. The storage unit for storing an intake cutoff valve so as not to block the intake passage, and the intake cutoff valve is stored in the storage unit during operation of all cylinders.
A variable cylinder control device for an odd-numbered multi-cylinder engine described in. 3. The odd number multiple according to claim 1, wherein a bypass passage for bypassing the intake passage provided with an intake cutoff valve is provided, and intake is performed through the bypass passage during all cylinder operation. Variable cylinder control device for cylinder engine. 4. A phase varying means for changing the phase of the intake cutoff valve is provided so that the intake cutoff valve does not always cut off the intake passage each time the intake stroke arrives during operation of all cylinders. 2. The variable cylinder control device for an odd multi-cylinder engine according to claim 1, wherein the phase of the intake cutoff valve is shifted.