JPS5963336A - Valve opening degree control device in carburettor - Google Patents

Abstract

PURPOSE:To enable a valve opening degree control device of a small-sized structure to control a closing valve in a wide range with a high degree of accuracy, by providing, in the closing valve of a carburettor, a valve drive device comprising a cam rotated by a control engine, a follower arm swing by the cam and a gear mechanism. CONSTITUTION:A gear 22 which is attached to the valve shaft 7 of a throttle valve 6 disposed in an intake-air passage A in a carburettor 1, is driven to rotate by means of a follower arm 24 abutted at its one end against a cam plate driven by a control engine 46 and as well a gear integral with the arm 24. The follower arm 24 swings about a pivotal shaft 23 as a pivotal point. Accordingly, even if a valve opening degree control device is a small-sized, the opening degree of a closing valve may be controlled over a wide range.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention aims to reduce the flow rate of intake gas in the intake tract to 1ill side.
The present invention relates to a valve control device for a carburetor, which is equipped with a mechanism for controlling the opening degree of an on-off valve by 11 degrees using a control motor.

Conventionally, the opening degree of an on-off valve such as a choke valve or a throttle valve that controls the flow rate of intake gas in the intake tract of a carburetor has been conventionally controlled.
Q] In a mechanism for control by a prime mover, the control prime mover rotates a cam/plate, and the cam control force from this cam plate is applied to an on/off valve such as a choke valve or a throttle valve through only a link mechanism. As a result, the opening degree of the on-off valve was increased by 1tllml.

However, in order to control the opening degree of the on-off valve over a large range, the link machine #I has to be made larger.Also, as long as only the link mechanism is used, it is difficult to maintain accuracy over a wide range of the opening degree of the on-off valve. There is a limit to controlling the opening of the on-off valve, and the torque between the input force law torque of the link mechanism and the torque on the output side is The ratio cannot be kept constant.

Therefore, the main object of the present invention is to create a valve opening for a carburetor that can control the opening K of the on-off valve over a wide range with high accuracy even with a small structure. The aim is to obtain a lil° control device.

According to the present invention, the valve opening degree ηIJ control device for a carburetor is configured to rotate around a pivot shaft of a driven arm that is swung with its distal end abutting against the cam surface of a cam plate that is rotationally driven by a control engine.

The on-off valve is equipped with a drive-side pawl that rotates integrally with the driven arm, and a driven-side gear for rotating and driving a valve shaft of an on-off valve such as a choke valve or a throttle valve. , opening and closing are controlled through the meshing of the drive-side gear and the driven-side gear.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A vaporizer to which all embodiments of the present invention are applied will be described in detail below with reference to the drawings.

First, in FIGS. 1 to 3, the intake path A of the carburetor 1
A fuel nozzle 3 is disposed in the center of the venturi portion 2 formed in the venturi, and a choke valve 4 is supported by a choke valve shaft 5 on the upstream side of the fuel nozzle 3. Throttle valve 6 is located downstream of 3.
is carried by the throttle valve 1lIll]7.

A secondary intake passage B is formed in a position adjacent to the intake passage A, and the secondary throttle valve in this secondary intake passage B is opened and closed by a secondary throttle valve switch 8 to open and close the engine. The engine is configured to be able to replenish the secondary air-fuel mixture into the combustion chamber of the engine in the high-speed rotation region of the engine, thereby increasing the cylinder filling efficiency. Such a secondary intake tract B
The secondary air-fuel mixture replenishment device comprising the secondary throttle valve opener 8 and the like is conventionally well known and has no direct relation to the present invention, so it will not be described in further detail.

The choke valve 11q115 is eccentric from the center of the choke valve 4, so that when the choke valve 4 is closed, engine suction negative pressure acts on the choke valve 4 as opening torque.

Further, the choke valve shaft 5 extends from inside the intake passage A to the outside, and this choke valve! 1+1115 extends outward from the intake path A, one end is locked to the outer wall surface of the intake &A, and the other end (i!II is locked to the choke valve shaft 5). As a result, a return spring 9 that exerts a bias rotational force ffi+J on the choke valve shaft 5 so as to always open the choke valve 4 toward the maximum opening position, and a follower spring 9 that follows the cam surface of a first cam plate 59 (described later) at the tip thereof. roller 12
It integrally has a driven arm 11 equipped with a driven arm 11, and also integrally has a driven arm 13f, which has a following roller 14 at its tip that follows the cam surface of a second cam plate 60, which will be described later. By being pivotally supported on 5 for relative rotation,
A rocking plate 10 that transmits rotational force to a choke lever 17 (described later) via a claw 20 protruding from the outer periphery, and an interlocking plate 10 that moves forward and backward in conjunction with the rocking motion of a throttle lever (described later). A rotary plate 15 whose one end side is pivotally supported and which rotates integrally with the choke valve shaft 5 by being fixed to the choke valve shaft 5; and a pawl 1 that abuts the pawl 20 of each moving plate 10.
9 and is fixed on the choke valve shaft 5, the choke lever <-17 is locked on one end side to the claw 20, and the other end side is locked on the choke lever 17, so that the claw is always engaged. A biasing spring 18 is provided so that the biasing spring 18 is biased in the direction in which the claw 20 and the claw 19 come into contact with each other.

The throttle valve shaft 7 also extends from the inside of the intake passage A to the outside, and the part of the throttle valve shaft 7 that extends outward from the intake passage A has a -☆1 ( A1μjl The force ball is locked to the outer wall surface to the intake passage, and the end side is locked to the gear 22 (described later). Figure and 4th
In the figure, a return spring 21 applies bias rotational force in the counterclockwise direction, and the throttle valve shaft 7'' is pivotally supported so as to be rotatable relative to the throttle valve shaft 7. 23, the sector gear is formed on the proximal end side of the driven arm 24, and the distal end thereof is provided with a tracking roller 26 that follows the cam surface of a third cam plate 61, which will be described later. 25 and the gear 22 meshing with the throttle valve shaft I.
It is supported on the throttle valve shaft I so that it can rotate relative to the gear 22, and is fixed to the gear 22 side via a spacing plate 27 so that it can swing integrally with the gear 22. The throttle drive lever 28 and the throttle wire 4, as shown in detail in FIG.
2, and has a guide groove 41 for guiding the throttle wire 42, as shown in FIG. 42, the throttle valve shaft 7 is moved clockwise in the direction shown in FIG. 3 or 4 (( A throttle wire is fixed on the throttle valve shaft 7 so as to rotate, and further, as shown in FIG. 38 are arranged.

In FIGS. 1, 3, and 4, the throttle drive lever 28 swings around the throttle valve shaft 7 in conjunction with a control motor 46, which will be described later, which operates according to a human control signal. The swing limit of the dollar lever 38 in the direction of decreasing the opening degree of the throttle valve 6 is restricted. The regulating force transmitting part between the throttle valve and the throttle dry lever 28 includes at least one of the throttle valve and the throttle drive lever.
[Second 1] For example, as shown in the diagram, the throttle drive breech -2
A buffer device C is interposed to cushion the impact between the throttle valve and the drive shaft 28 while being supported by the shaft 111 of the shaft 8.

In the loosening device C, the throttle dry valve 28
An adjusting screw 31 with a male thread of 75 mm on the base end is loosely fitted into a loosely fitting hole drilled at the bent portion 29 formed at the tip of the FJ!3. Mu: J.
11, an adjustment nut 30 is screwed into the retainer 1'' which protrudes outward from the bent portion 29 of the bolt 31 (V
On the proximal end surface of the N21 adjustment screw 310, an adjustment groove 32 with a diameter of ζ is formed to engage two tools such as a dryer. The tip of the adjustment screw 31 is the throttle v ]'
3 8 (projecting toward the contact part 39 of 1'.li,
A cylindrical abutment 34 having an umbrella portion 3511 at the tip is attached to the tip of the adjustment screw 31.
The im side [fits the f-th position in the phrase freely. Contact piece 34
In the body of the body, axially long lengths 36 and 36' of the abutting element 34 are bored at diametrically opposed positions, respectively, and a part near the tip of the adjusting screw 31 is provided with a long length 36, 36'. is 1
A pin 33 that penetrates and projects in the radial direction is fixed, and the protruding portions at both ends of this pin 33 fit into each elongated hole 3 of the contact element 34.
6, 36'. And, between the umbrella part 35 of the abutting element 34 and the bending part 29, there is an 'i' l1 emitted f.

A spring 3Y is interposed therebetween, and the abutting element 34 is always springed toward the tip j7iM of the adjustment screw 31 due to the spring action of the spring 37.

In FIG. 1 and FIG. 2, each intake passage A of the carburetor 1,
Support arms 43 and 44 are mounted on the outer wall of H, and are configured by, for example, a pulse motor. IIAI
A transmission section outer frame 45 supporting a prime mover 46 is supported. The inside of the control 1 prime mover 46 and the transmission part chamber surrounded by the transmission part outside ν~45 are bounded by a common J wall, that is, a common partition wall 47, and the output shaft 48 of the production 1 prime mover 46 and , gear '11156.57H1 of each float 53, 54.55 of the reduction float train 50 in the transmission chamber
Both are rotatably supported by an 'IQII receiving portion formed within the common partition wall 47.

In other words, the output of one control motor 46] The bolt 48 projects into the transmission chamber while being supported by a bearing 49 supported by a common gap A147. A gear 52 fixed to the tip of the 4Qt+ 48 meshes with a gear 53 fixed on a gear 11i11156 whose one end side is pivotally supported by a bearing formed in the common partition wall 47. And gear lll1
Another gear 54 fixed on the gear shaft 56 is meshed with the East Army 55 (fixed on a gear shaft 57 whose one end side is supported by the IIQ11 by a bearing portion formed in the common bulkhead 47).

The control motor 46 is, for example, a pulse motor, and the engine water temperature A! Forward rotation pulse or reverse rotation pulse that is an output signal of an electronic control circuit (not shown) that operates based on input factors such as engine temperature, engine rotation speed, and engine intake air temperature detected through f. 7 after receiving the entire application of
It is driven to rotate, and its output torque is transmitted through the entire reduction gear train 50 to the start of the electromagnetic clutch 51 inside the transmission section outer frame 45.

As shown in FIGS. 1, 2, and 5, the drive shaft 58, which is the output shaft of the electromagnetic clutch 51, protrudes parallel to the choke valve shaft 5 and the throttle valve shaft 7. Drive l! +1lI58 includes a displacement detection plate 62 for detecting rotational displacement, a collar 63, a third cam plate 61, a collar 64, a second cam plate 60, and a collar 6.
5 and the first cam 4 59 are fitted using their fitting holes. At this time, a flat portion 58, a is formed over the entire length of the protruding portion of the drive shaft 58 in a portion facing the drive shaft 58 in the diametrical direction, and a displacement detection plate 62,
The fitting holes of the third cam plate 61, the second cam plate 60, and the first cam plate 59 are shaped to match the cross-sectional shape of the drive shaft 58. Since the drive shaft 58 has such a flat portion 58a, the rotational torque of the first viewing shaft 58 can be effectively applied to the displacement detection plate 62 and each cam plate 59, 6.
0.61.

In addition, a pair of pin insertion holes 66 and 66' are formed in the displacement detection plate 62, sandwiching the fitting hole, and a pair of pin insertion holes 67 and 67' are formed in the collar 63 at positions facing each other in the diametrical direction. A pair of pin insertion holes 68, 68' are formed in the third cam plate 61, sandwiching the fitting hole, and a pair of pin insertion holes 69, 69' are formed in the collar 64 at positions facing each other in the diametrical direction. A pair of pin insertion holes 70.70' are formed in the second cam plate 60 to sandwich the fitting hole, and a pair of pin insertion holes 71.71' are formed in the collar 65 at positions facing each other in the diametrical direction. Furthermore, a pair of pin insertion holes 72, 72' are formed in the first cut and plate 59 with the fitting holes 66, 67, 68, 69, 70, 71. and 72
An insertion pin 73 is inserted through each of the pin insertion holes 66', 67', 68', 69', 70.
'.

11' and 72' have insertion pins 73. ' is inserted.

These pair of insertion pins 73, 73'id, each cam plate 59
．． 60, 61 and the displacement detection plate 62, and constitutes a phase shift prevention means for performing nom control and displacement detection with high accuracy. As a phase shift prevention means, inserts as shown in [1], Ebi7□3, 73,
1. Yo-A, I, ゎ9゜4.4 cutlet & 59.60.6
1 and the displacement amount detection plate 62 so as not to cause a relative phase shift (f may be tightly fixed.
A male thread is formed at the tip of the N+ 5g, and by tightening the γ4 screw completely to this male thread, each cam plate 59, 60, 61 and displacement can be detected. Plate 62 is securely mounted on drive shaft 58.

As shown in Figures 1 to 3, the first cutlet and temporary 5
9 is located at an axial position corresponding to the following roller 12 of the driven arm 11, and the second cam plate 60 is located at a position corresponding to the following roller 14 of the driven arm 13.
The third cam plate 61 is located at an axial position corresponding to , and the third cam plate 61 is located at a position in the +11+ direction corresponding to the following roller 26 of the driven arm 24 .

In FIGS. 1 to 3 and 6, a female threaded portion 77 formed on the outer frame 45 of the transmission part has a throttle valve shaft 7.
A /ξjt threaded portion 76 is formed on the proximal end side of a rotating shaft 75 parallel to 1. An adjustment groove 78 is formed on the proximal end surface of the rotating shaft 75, in which a tool such as a screwdriver can be engaged, and the driven arm 24 is pivotally supported on the distal end surface of the rotating shaft 75. The pivot shaft 23 is parallel to the rotation shaft 75, and the center axis of the pivot shaft 23 is offset from the center axis of the rotation shaft 75 by a distance Δ 72p, and is integrally connected to the rotation shaft 75.

A cylindrical member 79 is rotatably fitted onto the pivot shaft 23, and an intermediate portion of the driven arm 24 is fixed to the cylindrical member 19. The driven arm 24 has a pivot point IIη on one end side.
1123 and is locked to the Buhi end plate 80,
Due to the action of the biasing spring 81 whose other end is locked to the driven arm 24, the meshing angle between the weakly shaped push wheel 25 and the gear 22 is always in one direction. It is subjected to a biasing force in the direction. In other words, the biasing springs 81i-j constitute a backcracking direction maintaining mechanism for eliminating uneven meshing between the fan-shaped teeth jF 25 and the gear 22.

In addition, the tool is held in the adjustment groove 78 and rotated by 11tll+.
15, the pivot shaft 23 swings around the center axis of the rotation shaft 75, and as a result, the sector gear 25 and the tooth IC 22
Since the backlanonoyu meter of the meshing with is changed,
It is possible to adjust the packing mechanism of meshing between the sector gear 25 and the gear 22 by fully utilizing the adjustment mechanism 1rj7B.

That is, the eccentricity 111 caused by the rotation shaft 15 and the pivot shaft 23
The Il structure forms a backlash adjustment mechanism fl'/j.

Next, the operation of the illustrated vaporizer 1 will be explained.

First, at the time of first idle, that is, at the time of starting, the control prime mover 46 constituted by, for example, a pulse motor.
is driven in the forward direction, the rotation torque of the control motor 46 is transmitted to the drive shaft 58 via the reduction gear train 50 and the electromagnetic clutch 51, and the drive shaft 58 is rotated in the normal direction.
B is rotated in the counterclockwise direction in FIG.

, the first cam plate 59 rotates as the drive +Il+ 58 rotates.
, second cam plate 60, third cam plate 61, and displacement detection plate 6
2 rotates integrally with the drive 'l1lI+ 58,
At this time, since the first cut/plate 59 and the second cam plate 60 are arranged out of phase in the rotational direction, the cam surface of the first cam plate 59 hits the follower roller 12 first. Followed arm 11
The rocking plate 10 is rocked clockwise in FIG.
The rocking plate 10ff is further rocked clockwise in FIG. 3 via the driven arm 13. As a result, nail 20
, the choke valve shaft 5 is returned to the position 3 through the biasing spring 18, the pawl 19, and the choke lever 1γ against the elastic force of the return spring 9.
By rotating clockwise in the figure, the choke valve 4 is rotated to the closed position.

During this time, the cam surface of the third cam plate 61 is constantly in contact with the following roller 26, causing the driven arm 24 to swing counterclockwise in FIG. 3 around the pivot 23. Accordingly, the sector gear 25 and the 92 are rotated clockwise in FIGS. 3 and 4 around the throttle valve shaft 7 against the spring force of the return spring 21, and as the gear 22 rotates, ,
The throttle drive lever 28 is swung clockwise in FIGS. 3 and 4 around the throttle valve shaft 7 integrally with the gear 22. And throttle drive lever 2
8 presses the still-contacting part 39 of the throttle lever 38 via the shock absorber C, so that the throttle lever 38 is centered around the throttle valve shaft 7 against the spring force of a return spring (not shown). As shown in FIGS. 3 and 4, it is swung clockwise.

As a result, the throttle valve shaft 7 rotates clockwise in FIGS. 3 and 4 together with the throttle lever 38, so that the throttle valve 6 opens to the noast idle opening position.

After the engine is started, the suction negative pressure acts on the choke valve 4 as an opening torque, and this opening torque opens the spring to prevent the air-fuel mixture created in the intake passage A from becoming over-enriched.

After the engine starts, when the temperature of the engine rises and exceeds the set temperature, the control engine 46 is driven in reverse, and accordingly, the drive shaft 58 is driven through the reduction gear train 5o and the electromagnetic clutch 51.
is rotated clockwise in FIG. And the first
The cam plate 59, the second cut/plate 60, the third cam plate 61, and the displacement detection plate 62 rotate integrally with the drive '11Ill5B in different directions at different times in FIG. Due to the spring force 9, the rocking plate 10 is moved against the choke valve shaft 5.
, choke lever 17, pawl 19, biasing spring 18 and pawl 2
3 in the counterclockwise direction in FIG. The choke valve 1tt+
As s rotates counterclockwise in FIG. 3, the opening degree of the choke valve 4 increases.

During this time, the follower roller 26 moves along the cam surface of the third cam plate 61, and the driven arm 24 moves around the pivot shaft 23.
It is swung clockwise in the figure. Along with this, the sector gear 25 receives the spring force of the return spring 21 from the gear 22.
3 and 4 around the throttle valve shaft 7, the throttle drive lever 28 integrally rotates around the throttle valve shaft 7 in the counterclockwise direction in FIGS. 3 and 4. Rocks clockwise.

As a result, the throttle lever 38 swings counterclockwise in FIGS. 3 and 4 due to the spring force of a return spring (not shown), and the throttle valve shaft 7 accordingly swings in the counterclockwise direction as shown in FIGS. 3 and 4. By rotating counterclockwise in the figure, the throttle valve 6 is closed to the normal idle opening position.

During idle control when the engine is connected to the full load of auxiliary equipment such as a car cooler compressor,
As the control motor 46 is further reversed and driven, the drive shaft 58 further rotates clockwise in FIG. 3. Then, as the third cam plate 61 further rotates clockwise in FIG.
In the figure, it is swung counterclockwise. the result,
Gear 22, throttle drive lever 28.1litj
The throttle valve shaft 7 is rotated clockwise in FIGS. 3 and 4 via the device C and the throttle levers 3B', +1-, and the throttle valve 6 is rotated in the direction of increasing the opening.

During autocruise, that is, when driving at a constant speed, the carburetor 1 basically operates in the same manner as during idle control, but at this time, the opening degree of the throttle valve 6 (
Jt is set to be larger than the opening degree during idle control.

During normal operation, the throttle lever 38 is swung around the throttle valve 11117 via the throttle lever 42 according to the driver's operation, and the opening degree of the throttle valve 6 is accordingly adjusted based on the driver's will. be done. At this time, the shock absorber C does not function as a strainer for the contact portion 39, and limits the swinging limits of the throttle drive lever 28 (i) and the throttle lever 38 in the opening and decreasing directions of the throttle valve 6. The swinging of the throttle lever 38 in the direction of increasing the opening of the throttle valve 6 causes the rotation root 15 to become a choke valve via the interlocking link 16! The choke valve 4 is rotated counterclockwise in FIG. 3 about the center, and as a result, the opening of the choke valve 4 is fully increased so that the amount of suction air does not become too small.

In the illustrated carburetor 1, the force opening control device according to the present invention is applied only to the measured value of the throttle valve opening. In addition to 1flJ fall, the valve opening secondary device 1 according to the present invention can be modified to some extent and applied to choke valve opening control without completely changing the basic idea.

As described above, according to the present invention, the carburetor 7-11 valve P opening degree control device has a driven arm whose tip end is swung by the cam of the cam plate which is rotated and driven by the control motor. The on-off valve is equipped with a gear on the drive side that rotates integrally with the driven arm around the pivot point Iil+, and a full wheel on the driven side for rotating and driving the valve shaft of the on-off valve. By, motion (1
Opening and closing is controlled through the meshing of the tooth 1]'j on the driven side and the tooth 11L on the driven side, so one valve opening control device is small.
Even if the valve is made of IQ('F'L-type), it is possible to control the opening of the on-off valve with precision of 41αl/-1.

[Brief explanation of the drawing]

Fig. 1 shows a partial cross-section of a carburetor to which one embodiment of the present invention is applied; Fig. 11: Fig. 2; A partially cross-sectional side view of the carburetor in Figure 1, an enlarged view of a part of the carburetor in Figures 4C and 3,
Figure 5 is a perspective view of the cam portion of Figure 1; Figure 6 is;
This is an enlarged view of a portion of Figure 1. ...Opening side J prime mover 61...Cam plate A...Intake tract Dear Commissioner of the Japan Patent Office 1. Indication of the case 1982 Patent Application No. 174743 2 Name of the invention Valve opening control device for carburetor 3 Relationship with the case of the person making the amendment Patent applicant name (532) Honda Motor Co., Ltd. 4, representative
Address: 4-4-5 Shinbashi, Minato-ku, Tokyo Date of amendment order for No. 1 Ninomura Building 5

Claims (1)

[Claims] An on-off valve (6) that controls the flow rate of intake gas in the intake path (A)
) is a mechanism in which the opening degree of the cam plate (61) is controlled by a control motor (46), the tip of which is in contact with the cam surface of a cam plate (61) that is rotationally driven by the control motor (46). A driving side gear (25) rotates integrally with the driven arm (24) around the pivot shaft (23) of the driven arm (24) that is oscillated, and a valve shaft (7) of the on-off valve (6). ) and a gear (22) on the driven side for rotating and moving, and the on-off valve (5) is equipped with a gear (25) on the drive side and a jig (22) on the driven side.
2) A valve opening control device for a carburetor that is controlled to open and close through engagement with the valve.