JP4378310B2 - A pivoting device on the same axis of the speed adjustment lever and the engine stop lever of a diesel engine - Google Patents

Description

  The present invention relates to a pivoting device on the same axis of a speed adjusting lever and an engine stop lever of a diesel engine.

[Prerequisite configuration]
For example, as shown in FIG. 1 to FIG. 3 (present invention) or FIG. 6 (prior art), the pivoting device on the same axis center of the speed adjusting lever and the engine stop lever of the diesel engine of the present invention is as follows. It is intended for those with the premise structure.

1 to 3 show Embodiment 1 of a pivoting device on the same axis of a speed adjusting lever and an engine stop lever of a diesel engine according to the present invention. FIG. 1 is a longitudinal front view of the pivoting device, and is an enlarged detailed view of a portion indicated by an arrow I in FIG. 2 is a cross-sectional plan view showing a governor device portion of a horizontal diesel engine, and FIG. 3 is a longitudinal front view of FIG.
FIG. 6 is a longitudinal front view of a pivoting device on the same axis center of a speed adjusting lever and an engine stop lever of a conventional diesel engine, and corresponds to FIG.

A cylindrical outer shaft (3) is passed through a bearing boss (2) of a fixed wall (1) of a diesel engine and is pivotally supported so as to be reciprocally rotatable. An inner shaft (4) is passed through the cylindrical outer shaft (3) and is pivotally supported so as to be reciprocally rotatable.
While the outer shaft output lever (5) is fixed to the inner end of the cylindrical outer shaft (3) protruding from the bearing boss (2) to the inner side of the fixed wall (1), the fixed wall (1) An outer shaft input lever (6) is fitted on the outer end of the cylindrical outer shaft (3) protruding outward from the outer periphery of the cylindrical outer shaft (3) so as to be relatively non-rotatable and slidable.

  The inner shaft output lever (7) is fixed to the inner end of the inner shaft (4) protruding from the cylindrical outer shaft (3) to the inside of the fixed wall (1), whereas the fixed wall (1 The inner shaft input lever (8) is fitted on the outer end of the inner shaft (4) projecting outward from the outer shaft so as not to be relatively rotatable.

  Of the outer shaft output lever (5) and the inner shaft output lever (7), one of the levers (5) and (7) serves as a speed adjustment output lever from the low speed rotation position (45) to the high speed rotation position. The other lever (7) and (5) are configured to be capable of reciprocatingly swinging to (46), while the other lever (7) and (5) are used as an engine stop output lever to release the stop device (11) for stopping the engine of the governor (9) It is configured to be operable from the position (12) to the stop operation position (13). A governor spring (10) of a governor device (9) provided inside the fixed wall (1) is engaged with the speed adjusting output lever.

  Correspondingly, one of the outer shaft input lever (6) and the inner shaft input lever (8), one of the levers (6) and (8) is a speed adjusting input lever, The other levers (8) and (6) are configured to operate the input levers (6) and (8) as engine stop input levers.

[Conventional technology]
In the above premise configuration, there is a prior art shown in FIG.
FIG. 6 is a longitudinal front view of a pivoting device on the same axis center of a speed adjusting lever and an engine stop lever of a conventional diesel engine, and corresponds to FIG.

A nut (81) is screwed to the upper end portion of the cylindrical outer shaft (3). By pressing the outer shaft input lever (6) against the bearing boss (2) with this nut (81), the outer shaft input lever (6) and the outer shaft output lever (5) are moved against the bearing boss (2). ).
The inner shaft input lever (8) is fixed to the upper end portion of the inner shaft (4) with a snap pin (82). The inner shaft output lever (7) is twisted against the outer shaft input lever (6) with a spring force that pushes the inner shaft input lever (6) upward by the compression coil spring (83), so that the inner shaft output lever (7) is Friction contact with the lower end surface of 3).

  The torsion and compression coil spring (83) has one end (84) of the spring locked to the input lever (8) for the inner shaft, whereas the other end (85) of the spring is the input lever for the outer shaft. By engaging with (6), the outer shaft output lever (5) is elastically pressed from the operation position side to the return position side, and the inner shaft output lever (7) is elastically pressed from the operation position side to the return position side. It is comprised as follows.

[Problems of conventional technology]
The above prior art has the following problems.
[Problem a. It is difficult to force and fix the inner shaft input lever (8) and the inner shaft output lever (7) with high precision and force. ]

  The force that frictionally fixes the inner shaft input lever (8) and the inner shaft output lever (7) is, firstly, the inner shaft output lever (7) and the lower end surface of the cylindrical outer shaft (3). Secondly, the force to contact the inner shaft output lever (7) and the cylindrical outer shaft (3) is the spring of the torsion and compression coil spring (83). Since the inner shaft input lever (8) and the inner shaft output lever (7) are relatively weak due to the force, it is difficult to strongly fix the force with high accuracy.

  [Problem b. The configuration for friction-fixing the outer shaft output lever (5), outer shaft input lever (6), inner shaft output lever (7), and inner shaft input lever (8) consists of the nut (81). Since the structure for screw fitting and the structure for elastic force of the torsion and compression coil spring (83) are required separately, the structure becomes complicated. ]

As a configuration for friction-fixing the outer shaft output lever (5) and the outer shaft input lever (6), a screw fitting structure of the nut (81) is required. Further, as a configuration for friction-fixing the inner shaft output lever (7) and the inner shaft input lever (8), a structure for repressing the torsion and compression coil spring (83) is required.
As described above, the configuration for friction-fixing the outer shaft output lever (5) / outer shaft input lever (6) and the inner shaft output lever (7) / inner shaft input lever (8) is a nut. Since the structure for screw fitting (81) and the structure for compression of the torsion and compression coil spring (83) are required separately, the structure becomes complicated.

  [Problem c. Setting the proper return spring force for the outer shaft required for the outer shaft output lever (5) and outer shaft input lever (6) to a precise value with high accuracy, and the inner shaft output lever (7) and inner shaft Setting the proper return spring force for the inner shaft required for the shaft input lever (8) to an accurate value with high accuracy cannot be achieved by the torsion and compression coil spring (83). ]

  Appropriate return spring force for the outer shaft necessary for pressing the outer shaft output lever (5) and the outer shaft input lever (6) toward the return position (45), an inner shaft output lever (7), and The proper return spring force for the inner shaft required to repress the inner shaft input lever (8) toward the return position (12) is a function required for the speed adjustment lever and a function required for the engine stop lever. Therefore, the appropriate return spring forces for the outer shaft and the inner shaft are different from each other.

In the above prior art, the torsion and compression coil spring (83) represses the outer shaft output lever (5) from the operation position side to the return position side, and the inner shaft output lever (7) from the operation position side. It is configured to repress toward the return position.
Therefore, the appropriate return spring force for the outer shaft required for the outer shaft output lever (5) and the outer shaft input lever (6) is set to an accurate value with high accuracy, and the inner shaft output lever ( 7) and setting the proper return spring force for the inner shaft required for the inner shaft input lever (8) to an accurate value with high accuracy cannot be achieved by the torsion and compression coil spring (83). .

An object of the present invention is to do as follows.
[I]. With the high-precision and strong axial force by tightening the double nut, the outer shaft output lever and the outer shaft input lever are held in contact with the bearing boss and firmly fixed to the target value with high accuracy. The shaft output lever and the inner shaft input lever are held in contact with both the cylindrical outer shaft and the outer shaft input lever so that the target value can be fixed with high precision and force at the same time. .

  [B]. The first fine adjustment tightening structure for friction-fixing the outer shaft output lever and the outer shaft input lever to the target value with high accuracy, and the inner shaft output lever and the inner shaft input lever with the target value with high accuracy The second fine-adjusting tightening configuration for frictional fixing to both the configuration and the operation for both the first and second fine-adjusting tightening operations is halved by using a pair of lock nuts.

[C]. The appropriate return spring force for the outer shaft required for the outer shaft input / output lever must be set to an accurate value with high accuracy by the outer shaft return spring, and the inner shaft appropriate for the inner shaft input / output lever. The return spring force is set to an accurate value with high accuracy by the return spring for the inner shaft.
[D]. When the engine is running at low speed, the tension of the return spring for stopping the engine is set to the reference tension state, and the engine is stopped with a relatively light force. At the time of high speed operation, the tension of the return spring for stopping the engine is set to increased tension. It is possible to achieve a strong prevention of malfunction of engine stop due to disturbance force.

  [E]. Rust and fine dust generated between the outer shaft outer end side and the inner shaft are floated in the outer clearance gap or the inner clearance gap to prevent friction between the engagement surfaces. This eliminates the trouble of operating the speed adjustment input lever and the engine stop input lever. In addition, even when the cylindrical end wall portion near the opening end of the outer end portion of the cylindrical outer shaft is slightly deformed by an external force, the outer clearance gap having a large gap absorbs the deformation margin, Eliminates the trouble of operating the speed adjustment input lever and engine stop input lever.

[F]. By covering the outer periphery of the outer end of the outer shaft with the waterproof cylinder of the inner shaft input lever, fine dust and moisture in the air in the outer space are placed between the outer shaft outer end and the inner shaft. Prevents intrusion and eliminates problems in operating the speed adjustment input lever and engine stop input lever.
[G]. In addition to preventing fine dust and moisture in the outside air from entering the inside with the waterproof cylinder of the inner shaft input lever in advance, the O-ring prevents entry into the outer end portion of the outer shaft. Eliminates the trouble of operating the speed adjustment input lever and engine stop input lever.

  In order to solve the above problems, the pivotal support device on the same axis center of the speed adjusting lever and the engine stop lever of the diesel engine of the present invention is exemplified as shown in FIGS. The following feature configuration is added.

  1 to 5 show a first embodiment of a pivoting device on the same axis of a speed adjusting lever and an engine stop lever of a diesel engine according to the present invention. FIG. 1 is a longitudinal front view of the pivoting device, and is an enlarged detailed view of a portion indicated by an arrow I in FIG. 2 is a cross-sectional plan view showing a governor device portion of a horizontal diesel engine, and FIG. 3 is a longitudinal front view of FIG.

  4A is a sectional view taken along the line AA in FIG. 1, FIG. 4B is a sectional view taken along the line BB in FIG. 1, and FIG. 4C is an arrow C in FIG. FIG. FIGS. 5A and 5B are diagrams showing a state where the outer shaft input lever 6 and the inner shaft input lever 8 are switched from the states of FIGS. 4A and 4B, respectively.

The invention of claim 1. See FIGS.
The inner shaft input lever (8) is externally fitted to the inner shaft (4) so as not to rotate relative to the inner shaft (4), and approaches the inner shaft output lever (7) with a double nut (14). It is configured so that it can be pushed toward the side.

  By adjusting the pushing of the double nut (14), the distance between the inner shaft input lever (8) and the inner shaft output lever (7) is shortened via the inner shaft (4). The input lever (8) presses the outer shaft input lever (6) against the bearing boss (2), while the inner shaft output lever (7) turns the outer shaft output lever (5) into the bearing boss (2). Press. As a result, the outer shaft input lever (6) and the outer shaft output lever (5) are frictionally fixed to the bearing boss (2), and the outer shaft input lever (6) and the cylindrical outer shaft ( 3), the inner shaft input lever (8) and the inner shaft output lever (7) are fixed by friction.

O Invention of claim 2. See FIG. 1, FIG. 4 and FIG.
The invention of claim 2 is characterized in that, in the invention of claim 1, the following characteristic configuration is added.

  The outer shaft output lever (5) and the outer shaft input lever (6) are configured to be elastically pressed by the outer shaft return spring (15) from the operation position (46) side to the return position (45) side. The inner shaft output lever (7) and the inner shaft input lever (8) are configured to be elastically pressed from the operation position (13) side to the return position (12) side by the inner shaft return spring (16). It is characterized by.

The invention of claim 3. See FIG. 1, FIG. 4 and FIG.
The invention of claim 3 is characterized in that, in the invention of claim 2, the following characteristic configuration is added.

The outer shaft output lever (5), the outer shaft input lever (6), the outer shaft return spring (15), the return position (45), and the operation position (46) are respectively output to the speed adjustment output lever (5 ) ・ Speed adjustment input lever (6) ・ Speed adjustment lever return spring (15) ・ Low speed rotation position (45) ・ High speed rotation position (46).
The inner shaft output lever (7), the inner shaft input lever (8), the inner shaft return spring (16), the return position (12), and the operation position (13) are respectively connected to an engine stop output lever (7). The engine stop input lever (8), the engine stop lever return spring (16), the stop release position (12), and the stop operation position (13).

The spring base end portion (17) of the speed adjustment lever return spring (15) is locked to the fixed wall (1), and the spring free end portion (18) has a speed adjustment input lever (6) and a speed adjustment. Engage with one of the output levers (5).
A spring base end portion (19) of the engine stop lever return spring (16) is engaged with one of the speed adjustment output lever (5) and the speed adjustment input lever (6), and the spring The free end portion (20) is configured to be engaged with one of an engine stop output lever (7) and an engine stop input lever (8).

The invention of claim 4. See FIG.
The invention of claim 4 is characterized in that, in the invention of claim 1, 2, or 3, the following characteristic configuration is added.

  The outer periphery of the inner shaft (4) at a position that fits into the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) protruding from the bearing boss (2) to the outer space of the fixed wall (1). In the surface portion, a rear side relief circumferential groove (21), an O-ring groove (22), and an outer side relief circumferential groove (23) are successively formed in order from the side closer to the bearing boss (2) to the side farther from the side.

  An O-ring (24) is inserted between the O-ring groove (22) and the outer shaft outer end side portion (3a). The outer end portion of the outer relief circumferential groove (23) is positioned outside the outer end surface of the outer shaft outer end side portion (3a). The outer relief clearance (23A) between the outer relief circumferential groove (23) and the outer shaft outer end side portion (3a) is formed between the rear side relief circumferential groove (21) and the outer shaft outer end side portion (3a). It is characterized by being set to a gap larger than the back side clearance gap (21A).

The invention of claim 5. See FIG.
The invention of claim 5 is characterized in that, in the invention of claim 4, the following characteristic configuration is added.

The shaft centers of the bearing boss (2), cylindrical outer shaft (3) and inner shaft (4) are set up and down, and the speed adjusting input lever (6) and the engine stopping input lever (8) are It is located above the fixed wall (1).
The outer part (3a) on the outer end of the cylindrical outer shaft (3) protrudes upward from the input lever (6) for speed adjustment and covers the outer periphery of the outer end (3a) of the outer shaft. The cylinder portion (26) is fixedly extended downward from the engine stop input lever (8) toward the speed adjustment input lever (6) side, and the lower end surface of the waterproof cylinder portion (26) is input to the outer shaft. It touches the lever (6).

The invention of claim 6. See FIG.
The invention of claim 6 is characterized in that, in the invention of claim 5, the following characteristic configuration is added.

  A sealing seat surface (27) is formed at the back of the cylindrical hole of the waterproof cylinder portion (26) fixed to the lower portion of the inner shaft input lever (8), and the sealing seat surface (27) An O-ring (28) is inserted between the cylindrical outer shaft (3) and the upper end surface of the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3).

The pivoting device on the same axis center of the speed adjusting lever and the engine stop lever of the diesel engine of the present invention has the following effects.
The invention of claim 1. See Fig. 1-5.
[Effect a. The outer shaft output lever (5) and the outer shaft input lever (6) are clamped into contact with the bearing boss (2) by the high-precision and powerful axial force by tightening the double nut (14). The inner shaft output lever (7) and the inner shaft input lever (8) are connected to the cylindrical outer shaft (3) and the outer shaft input lever (6). It is possible to achieve both at the same time by pinching and touching both of them and fixing the target value with high precision and strong friction. ]

The invention of claim 1 has the following characteristic configuration.
The inner shaft input lever (8) is externally fitted to the inner shaft (4) so as not to rotate relative to the inner shaft (4), and approaches the inner shaft output lever (7) with a double nut (14). It is configured so that it can be pushed toward the side.

  By adjusting the pushing of the double nut (14), the distance between the inner shaft input lever (8) and the inner shaft output lever (7) is shortened via the inner shaft (4). The input lever (8) presses the outer shaft input lever (6) against the bearing boss (2), while the inner shaft output lever (7) turns the outer shaft output lever (5) into the bearing boss (2). Press. As a result, the outer shaft input lever (6) and the outer shaft output lever (5) are frictionally fixed to the bearing boss (2), and the outer shaft input lever (6) and the cylindrical outer shaft ( The inner shaft input lever (8) and the inner shaft output lever (7) are frictionally fixed to 3).

This characteristic configuration works as follows.
Firstly, the outer shaft output lever (5) and the outer shaft input lever (6) have the inner shaft by virtue of the powerful high-precision axial force generated by fine adjustment of the tightening operation of the double nut (14). Is sandwiched between the output lever (7) for the inner shaft and the input lever (8) for the inner shaft, and is firmly fixed to the bearing boss (2) by friction contact with the target value with high precision and, secondly, The inner shaft output lever (7) and the inner shaft input lever (8) are held in contact with both the cylindrical outer shaft (3) and the outer shaft input lever (6). Friction contact is strongly applied to the accuracy to fix the friction.

  As a result, the outer shaft output lever (5) and the outer shaft input lever (6) are clamped and abutted against the bearing boss (2) by the high-precision and powerful axial force by tightening the double nut (14). The inner shaft output lever (7) and the inner shaft input lever (8) are connected to the target value with high precision and strong friction, and the cylindrical outer shaft (3) and outer shaft input lever ( 6) It is possible to achieve both at the same time by pinching and fixing both to 6 and the target value with high precision and strong friction.

  [Effect b. First fine adjustment tightening structure for frictionally fixing the outer shaft output lever (5) and the outer shaft input lever (6) to the target value with high accuracy, the inner shaft output lever (7) and the inner shaft The second fine-adjusting tightening structure for accurately fixing the input lever (8) to the target value by friction is that both the first and second lock nuts (14) are used together. Both the configuration and operation for fine adjustment tightening can be halved. ]

O Invention of claim 2. See FIG. 1, FIG. 4 and FIG.
The invention of claim 2 has the following effects in addition to the effects [Effect A] and [Effect B] of the invention of claim 1.
[Effect C. Set the appropriate return spring force for the outer shaft required for the outer shaft input / output levers (6) and (5) to an accurate value with the outer shaft return spring (15). The proper return spring force for the inner shaft necessary for the output levers (8) and (7) can be set to an accurate value with high accuracy by the inner shaft return spring (16). ]

The invention of claim 2 has the following characteristic configuration.
The outer shaft output lever (5) and the outer shaft input lever (6) are configured to be elastically pressed by the outer shaft return spring (15) from the operation position (46) side to the return position (45) side. The inner shaft output lever (7) and the inner shaft input lever (8) are configured to be elastically pressed by the inner shaft return spring (16) from the operation position (13) side to the return position (12) side.

This characteristic configuration works as follows.
Appropriate return spring force for the outer shaft necessary for pressing the outer shaft output lever (5) and the outer shaft input lever (6) toward the return position (45), an inner shaft output lever (7), and The proper return spring force for the inner shaft required to repress the inner shaft input lever (8) toward the return position (12) is a function required for the speed adjustment lever and a function required for the engine stop lever. Therefore, the appropriate return spring forces for the outer shaft and the inner shaft are different from each other.

  The outer shaft appropriate return spring force required for the outer shaft output lever (5) and the outer shaft input lever (6) is set to an accurate value with high accuracy by the outer shaft return spring (15). The proper return spring force for the inner shaft required for the inner shaft output lever (7) and the inner shaft input lever (8) should be set to an accurate value with high accuracy by the inner shaft return spring (16). Can be made compatible.

The invention of claim 3. See FIG. 1, FIG. 4 and FIG.
In addition to [Effect A] and [Effect B] of the first aspect of the invention and [Effect C] of the invention of the second aspect, the invention of the third aspect has the following effects.

  [Effects d. When the engine is running at low speed, the tension of the return spring (16) for stopping the engine is in the standard tension state, and the engine is stopped with a relatively light force. It is possible to achieve both the fact that the tension increases and the malfunction of the engine stop due to the disturbance force can be strongly prevented. ]

The invention of claim 3 has the following characteristic configuration.
The outer shaft output lever (5), the outer shaft input lever (6), the outer shaft return spring (15), the return position (45), and the operation position (46) are respectively output to the speed adjustment output lever (5 ) ・ Speed adjustment input lever (6) ・ Speed adjustment lever return spring (15) ・ Low speed rotation position (45) ・ High speed rotation position (46).

  The inner shaft output lever (7), the inner shaft input lever (8), the inner shaft return spring (16), the return position (12), and the operation position (13) are respectively connected to an engine stop output lever (7). The engine stop input lever (8), the engine stop lever return spring (16), the stop release position (12), and the stop operation position (13).

The spring base end portion (17) of the speed adjustment lever return spring (15) is locked to the fixed wall (1), and the spring free end portion (18) has a speed adjustment input lever (6) and a speed adjustment. Engage with one of the output levers (5).
A spring base end portion (19) of the engine stop lever return spring (16) is engaged with one of the speed adjustment output lever (5) and the speed adjustment input lever (6), and the spring The free end (20) is configured to be engaged with one of an engine stop output lever (7) and an engine stop input lever (8).

This characteristic configuration works as follows.
Since the base end portion (19) of the engine stop lever return spring (16) is engaged with the speed adjustment input lever (6) or the speed adjustment output lever (5), the engine stop lever return spring is provided. The tension of (16) is higher than the reference tension state during low speed operation when the speed adjustment input lever (6) is set to the low speed rotation position (45). The spring tension increases when the tension is increased during high speed operation set in (46).

  Therefore, during low speed operation with the speed adjustment input lever (6) set at the low speed rotation position (45), the tension of the return spring (16) for stopping the engine is in the reference tension state. The stop operation force during low speed operation for operating the stop input lever (8) to the stop operation position (13) is a reference stop operation force, and the engine can be stopped with a relatively light stop operation force.

  Moreover, during high speed operation with the speed adjustment input lever (6) set at the high speed rotation position (46), the tension of the return spring (16) for stopping the engine is in the increased tension state. When a disturbance force is applied to cause the input lever (8) to malfunction to the stop operation position (13), the engine stop return spring (16) pushes the engine stop input lever (8) in the increased tension state. Since the engine is strongly held at the stop release position (12), it is possible to strongly prevent the engine from being erroneously stopped due to the malfunction of the engine stop input lever (8) due to the disturbance force.

  As described above, when the engine is operating at low speed, the tension of the return spring (16) for stopping the engine is in the reference tension state, and the engine is stopped with a relatively light force. It is possible to achieve both the fact that the tension of the spring (16) is in the increased tension state and the malfunction of the engine stop due to the disturbance force can be strongly prevented.

The invention of claim 4. See FIG.
In addition to the [Effect A] / [Effect B] of the invention of the above-mentioned Claim 1, the invention of Claim 4 has the following effect.

  [Effect E. Rust and dust generated between the outer shaft outer end side part (3a) and the inner shaft (4) are suspended in the outer clearance gap (23A) or the inner clearance gap (21A). Since no friction is generated between the fitting surfaces, it is possible to eliminate the troubles in the operation of the speed adjustment input lever (6) and the engine stop input lever (8). Moreover, even when the cylindrical end wall portion near the opening end of the outer shaft outer end side portion (3a) is slightly deformed by an external force, the outer clearance gap (23A) having a large gap absorbs the deformation margin. From this aspect as well, it is possible to eliminate the obstacles to the operation of the speed adjustment input lever (6) and the engine stop input lever (8). ]

Problems that the above-described premise configuration of the present invention has are as follows.
That is, between the fitting surface of the outer shaft outer end side portion (3a) projecting out of the bearing boss (2) of the cylindrical outer shaft (3) and the inner shaft (4) fitted therein, the fixed wall Fine dust or moisture in the air enters from the external space of (1), and the generation of moisture or dust bites between the fitting surfaces, so that the cylindrical outer shaft (3) and inner shaft (4) There is a problem that the operation of the speed adjustment input lever (6) and the engine stop input lever (8) is hindered by impairing the free relative rotation.

  Further, the cylindrical end wall portion near the opening end of the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) is first a weak end portion and secondly subjected to disturbance force. Thirdly, since it receives a force from the speed adjustment input lever (6) fitted on the third, it is in a condition that it is relatively easily deformed. When this cylindrical end wall portion is deformed, a large friction is generated with the inner shaft (4). From this surface as well, the speed adjusting input lever (6) and the engine stop input lever (8) There is a problem that hinders operation.

The invention of claim 4 has the following characteristic configuration in order to solve this problem.
The outer periphery of the inner shaft (4) at a position that fits into the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) protruding from the bearing boss (2) to the outer space of the fixed wall (1). In the surface portion, a rear side relief circumferential groove (21), an O-ring groove (22), and an outer side relief circumferential groove (23) are successively formed in order from the side closer to the bearing boss (2) to the side farther from the side.

  An O-ring (24) is inserted between the O-ring groove (22) and the outer shaft outer end side portion (3a). The outer end portion of the outer relief circumferential groove (23) is positioned outside the outer end surface of the outer shaft outer end side portion (3a). The outer relief clearance (23A) between the outer relief circumferential groove (23) and the outer shaft outer end side portion (3a) is formed between the rear side relief circumferential groove (21) and the outer shaft outer end side portion (3a). A clearance larger than the rear clearance (21A) is set.

This characteristic configuration works as follows.
Rust and dust generated between the outer shaft outer end side portion (3a) and the inner shaft (4) are suspended in the outer clearance gap (23A) or the inner clearance gap (21A). Since no friction is generated between the fitting surfaces, free relative rotation between the cylindrical outer shaft (3) and the inner shaft (4) is not impaired, and the speed adjusting input lever (6) and the engine stop are stopped. The trouble of operating the input lever (8) can be solved.

  Moreover, even when the cylindrical end wall portion near the opening end of the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) is slightly deformed by an external force, the outer clearance gap (23A ) Absorbs the deformation margin and eliminates or reduces the generation of large friction between the outer shaft outer end side portion (3a) and the inner shaft (4). It is possible to eliminate the problems that hinder the operation of the speed adjustment input lever (6) and the engine stop input lever (8).

The invention of claim 5. See FIG.
In addition to [Effect A] and [Effect B] of the invention of Claim 1 and [Effect E] of the invention of Claim 4, the invention of Claim 5 has the following effects.

  [Effects. Since the outer periphery of the outer shaft outer end portion (3a) is covered with the waterproof cylinder (6) of the inner shaft input lever (8), dust and moisture in the air in the outer space are on the outer shaft outer end side. Since it is prevented from entering between the fitting surfaces of the part (3a) and the inner shaft (4), the operation of the speed adjustment input lever (6) and the engine stop input lever (8) will be hindered. Can be eliminated. ]

The invention of claim 5 has the following characteristic configuration.
The shaft centers of the bearing boss (2), cylindrical outer shaft (3) and inner shaft (4) are set up and down, and the speed adjusting input lever (6) and the engine stopping input lever (8) are It is located above the fixed wall (1).

  An outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) is projected upward from the speed adjusting input lever (6). The waterproof cylinder (26) covering the outer periphery of the outer shaft outer end portion (3a) is fixedly extended downward from the engine stop input lever (8) toward the speed adjustment input lever (6). The lower end surface of the waterproof cylinder (26) was brought into contact with the outer shaft input lever (6).

This characteristic configuration works as follows.
The outer circumference of the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) is covered with the waterproof cylinder portion (6) of the inner shaft input lever (8) to be protected from the external space. Therefore, fine dust and moisture in the external space outside the fixed wall (1) are prevented from entering between the fitting surfaces of the outer shaft outer end side portion (3a) and the inner shaft (4). Therefore, from this aspect as well, it is possible to eliminate the obstacles to the operation of the speed adjustment input lever (6) and the engine stop input lever (8).

The invention of claim 6. See FIG.
In addition to [Effect A] and [Effect B] of the invention of Claim 1 above, [Effect E] of the invention of Claim 4 and [Effect F] of the invention of Claim 5, The following effects are produced.

  [Effects. Dust and moisture in the outside air are prevented from entering the inside by the waterproof cylinder part (26) of the inner shaft input lever (8), and the outer end part of the outer shaft by the O-ring (28). Since the intrusion into (3a) is prevented, it is possible to eliminate the obstacles to the operation of the speed adjustment input lever (6) and the engine stop input lever (8). ]

The invention of claim 6 has the following characteristic configuration.
A sealing seat surface (27) is formed at the back of the cylindrical hole of the waterproof cylindrical portion (26) fixed to the lower portion of the inner shaft input lever (8). An O-ring (28) was inserted and sandwiched between the sealing seat surface (27) and the upper end surface of the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3).

This characteristic configuration works as follows.
The dust and moisture in the air in the external space outside the fixed wall (1) are prevented in advance from entering the interior by the waterproof cylinder (26) of the inner shaft input lever (8). The outer shaft outer end side portion (3a) is formed by an O-ring (28) sandwiched between the sealing seat surface (27) in the cylinder portion (26) and the upper end surface of the outer shaft outer end portion (3a). ) And the inner shaft (4) are also prevented from entering between the fitting surfaces, which also interferes with the operation of the speed adjustment input lever (6) and engine stop input lever (8). You can eliminate the coming.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of a pivoting device on the same axis of a speed adjusting lever and an engine stop lever of a diesel engine according to the present invention will be described below with reference to the drawings.

Embodiment 1 See claim 1-5.
1 to 5 show a first embodiment of a pivoting device on the same axis of a speed adjusting lever and an engine stop lever of a diesel engine according to the present invention. FIG. 1 is a longitudinal front view of the pivoting device, and is an enlarged detailed view of a portion indicated by an arrow I in FIG. 2 is a cross-sectional plan view showing a governor device portion of a horizontal diesel engine, and FIG. 3 is a longitudinal front view of FIG.

  4A is a sectional view taken along the line AA in FIG. 1, FIG. 4B is a sectional view taken along the line BB in FIG. 1, and FIG. 4C is an arrow C in FIG. FIG. FIGS. 5A and 5B are diagrams showing a state where the outer shaft input lever 6 and the inner shaft input lever 8 are switched from the states of FIGS. 4A and 4B, respectively.

  2 and 3, reference numeral (31) is a cylinder block of a water-cooled diesel engine, (32) is a cylinder head, and (33) is a gear case. (34) is a piston, (35) is a crankshaft, (36) is a fuel injection pump, and (37) is a fuel metering rack. (38) is the crank gear, (39) is the centrifugal weight, (40) is the governor lever, (41) is the weight side lever, (42) is the spring side lever, (43) is the lever fulcrum shaft, (44) is the lever interlock It is a pin.

As shown in FIGS. 1 to 5, a cylindrical outer shaft (3) is passed through a bearing boss (2) of a fixed wall (1) made of an upper wall of a gear case (33) of a diesel engine so as to be reciprocally rotatable. Pivot. An inner shaft (4) is passed through the cylindrical outer shaft (3) and is pivotally supported so as to be reciprocally rotatable.
The outer shaft output lever (5) is fixed to the inner end of the cylindrical outer shaft (3) projecting downward from the bearing boss (2) to the inner side of the fixed wall (1). 1) An outer shaft input lever (6) is slidably mounted on the outer end of a cylindrical outer shaft (3) projecting upward to the outside by means of a flat fitting portion (55). Fit.

The inner shaft output lever (7) is fixed to the inner end of the inner shaft (4) projecting downward from the cylindrical outer shaft (3) to the inner side of the fixed wall (1). The inner shaft input lever (8) is fitted on the outer end portion of the inner shaft (4) protruding upward to the outside of (1) by the key (47) so as not to be relatively rotatable.
The outer shaft output lever (5) is configured as a speed adjusting output lever (5) that can reciprocally swing from the low speed rotation position (45) to the high speed rotation position (46). In contrast, the inner shaft output lever (7) serves as the engine stop output lever (7), and the engine stop passive device (11) of the governor device (9) is moved from the stop release position (12) to the stop operation position (12). Configure to be able to operate to 13). A governor spring (10) of a governor device (9) provided inside the fixed wall (1) is engaged with the speed adjusting output lever (5).

  Correspondingly, the outer shaft input lever (6) is a speed adjusting input lever (6), while the inner shaft input lever (8) is an engine stop input lever (8). The input levers (6) and (8) can be manually operated.

The feature of the first embodiment is obtained by adding the following feature configuration to the above premise configuration.
As shown in FIG. 1, the inner shaft input lever (8) is externally fitted to the inner shaft (4) so as to be relatively non-rotatable and slidable by a key (47), and a double nut (14 ) Is configured so that it can be pushed and adjusted closer to the inner shaft output lever (7).

By the pressing adjustment operation by screwing in the double nut (14), the distance between the inner shaft input lever (8) and the inner shaft output lever (7) is shortened via the inner shaft (4). The inner shaft input lever (8) presses the outer shaft input lever (6) against the bearing boss (2) with the friction plate (29) interposed therebetween, and at the same time, the inner shaft output lever (7) functions as the outer shaft output lever. (5) is pressed against the bearing boss (2) across the friction plate (30).
As a result, the outer shaft input lever (6) and the outer shaft output lever (5) are frictionally fixed to the bearing boss (2), and the outer shaft input lever (6) and the cylindrical outer shaft ( The inner shaft input lever (8) and the inner shaft output lever (7) are frictionally fixed to 3).

  The outer shaft output lever (5) and the outer shaft input lever (6) are configured to be elastically pressed by the outer shaft return spring (15) from the operation position (46) side to the return position (45) side. The inner shaft output lever (7) and the inner shaft input lever (8) are configured to be elastically pressed by the inner shaft return spring (16) from the operation position (13) side to the return position (12) side.

The outer shaft output lever (5), the outer shaft input lever (6), the outer shaft return spring (15), the return position (45), and the operation position (46) are respectively output to the speed adjustment output lever (5 ) ・ Speed adjustment input lever (6) ・ Speed adjustment lever return spring (15) ・ Low speed rotation position (45) ・ High speed rotation position (46).
The inner shaft output lever (7), the inner shaft input lever (8), the inner shaft return spring (16), the return position (12), and the operation position (13) are respectively connected to an engine stop output lever (7). The engine stop input lever (8), the engine stop lever return spring (16), the stop release position (12), and the stop operation position (13).

The speed adjusting lever return spring (15) is a torsion coil spring, and its spring base end (17) is engaged with a receiving wall (48) projecting from the fixed wall (1), and its spring play. The end (18) is engaged with the speed adjusting input lever (6).
The engine stop lever return spring (16) comprises a torsion coil spring, and its spring base end (19) is engaged with the speed adjusting output lever (5) and its spring free end (20) is It was configured to be engaged with an engine stop output lever (7).

  As shown in FIG. 45, the speed adjusting input lever (6) has a low speed limit bolt (50) or a limit contact piece (52) integrally formed therewith fixed to the fixed wall (1). By being received by the high speed limiting bolt (51), it is positioned at the low speed position (45) or the high speed position (46). The engine stop input lever (48) has a receiving piece (49) formed integrally therewith and is received by a receiving wall (48) fixed to the fixed wall (1). ).

  An interlocking engagement piece (53) is integrally formed with the speed adjustment output lever (5), and an interlocking engagement piece (54) is integrally formed with the engine stop output lever (7). As shown in FIG. 4, when the speed adjusting output lever (5) is operated from the high speed position (46) to the low speed position (45), the two interlocking engagement pieces (53) (54) are contacted. By interlocking, the engine stop output lever (7) is switched from the stop release position (12) to the stop operation position (13). Further, as shown in FIG. 5, when the engine stop output lever (7) is operated from the stop operation position (13) to the stop release position (12), the both interlocking engagement pieces (53) (54) The speed adjustment output lever (5) is switched from the low speed position (45) to the high speed position (46) by interlocking with the contact.

  As shown in FIG. 1, the space between the fitting surface between the upper portion of the bearing boss (2) and the cylindrical outer shaft (3) is sealed with an O-ring (58). The inner shaft (4) is positioned so as to be fitted into the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) projecting upward from the bearing boss (2) into the outer space of the fixed wall (1). The outer clearance groove (21), the O-ring groove (22), and the outer clearance groove (23) are successively formed in this order from the side closer to the bearing boss (2) to the side farther from the outer peripheral surface of the bearing. Do

An O-ring (24) is inserted between the O-ring groove (22) and the outer shaft outer end side portion (3a). The outer end portion of the outer relief circumferential groove (23) is positioned outside the outer end surface of the outer shaft outer end side portion (3a). The outer relief clearance (23A) between the outer relief circumferential groove (23) and the outer shaft outer end side portion (3a) is formed between the rear side relief circumferential groove (21) and the outer shaft outer end side portion (3a). A clearance larger than the rear clearance (21A) is set.
The shaft centers of the bearing boss (2), cylindrical outer shaft (3) and inner shaft (4) are set up and down, and the speed adjusting input lever (6) and the engine stopping input lever (8) are It is located above the fixed wall (1).

An outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) is projected upward from the speed adjusting input lever (6). The waterproof cylinder (26) covering the outer periphery of the outer shaft outer end portion (3a) is fixedly extended downward from the engine stop input lever (8) toward the speed adjustment input lever (6). The lower end surface of the waterproof cylinder (26) was brought into contact with the outer shaft input lever (6).
A sealing seat surface (27) is formed at the back of the cylindrical hole of the waterproof cylindrical portion (26) fixed to the lower portion of the inner shaft input lever (8). An O-ring (28) is inserted and clamped between the sealing seat surface (27) and the upper end surface of the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3). .

  The pivoting device on the same axis of the speed adjustment lever and the engine stop lever of the diesel engine of the present invention is, for example, a pivoting device on the same axis of the speed adjustment lever and the engine stop lever of the diesel engine. It is suitable for.

1 to 5 show a first embodiment of a pivoting device on the same axis of a speed adjusting lever and an engine stop lever of a diesel engine according to the present invention. FIG. 1 is a longitudinal front view of the pivoting device, and is an enlarged detailed view of a portion indicated by an arrow I in FIG. FIG. 2 is a cross-sectional plan view showing a governor device portion of a horizontal diesel engine. FIG. 3 is a longitudinal front view of FIG.

4A is a sectional view taken along the line AA in FIG. 1, FIG. 4B is a sectional view taken along the line BB in FIG. 1, and FIG. 4C is an arrow C in FIG. FIG. FIGS. 5A and 5B are diagrams showing a state where the outer shaft input lever 6 and the inner shaft input lever 8 are switched from the states of FIGS. 4A and 4B, respectively. FIG. 6 is a longitudinal front view of a pivoting device on the same axis center of a speed adjusting lever and an engine stop lever of a conventional diesel engine, and corresponds to FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Fixed wall, 2 ... Bearing boss, 3 ... Cylindrical outer shaft, 3a ... Outer shaft outer end side part, 4 ... Inner shaft, 5 ... Outer shaft output lever (speed adjusting output lever), 6 ... Outer shaft Input lever (speed adjustment input lever), 7 ... inner shaft output lever (engine stop output lever), 8 ... inner shaft input lever (engine stop input lever), 9 ... governor device, 10 ... governor spring 11 ... Passive tool for stopping the engine, 12 ... Stop release position (return position), 13 ... Stop operation position (operation position),

DESCRIPTION OF SYMBOLS 14 ... Double nut, 15 ... Outer shaft return spring (speed adjustment return spring), 16 ... Inner shaft return spring (engine return spring), 17 ... Spring base end, 18 ... Spring free end, 19 ... Spring base end part, 20 ... Spring free end part, 21 ... Back side relief circumferential groove, 21A ... Back side relief gap, 22 ... O-ring groove, 23 ... Outside relief circumferential groove, 23A ... Outside relief gap, 24 ... O Ring, 26 ... Waterproofing cylinder part, 27 ... Sealing seat surface, 28 ... O-ring, 45 ... Low speed position (return position), 46 ... High speed position (operation position).

Claims (6)

The cylindrical outer shaft (3) is passed through the bearing boss (2) of the fixed wall (1) of the diesel engine and is pivotally supported so as to be reciprocally rotatable. The inner shaft (4) is passed through the cylindrical outer shaft (3). And pivot to reciprocate freely,
While the outer shaft output lever (5) is fixed to the inner end of the cylindrical outer shaft (3) protruding from the bearing boss (2) to the inner side of the fixed wall (1), the fixed wall (1) The outer shaft input lever (6) is fitted on the outer end of the cylindrical outer shaft (3) protruding outward from the outer periphery so as to be relatively non-rotatable and slidable.
The inner shaft output lever (7) is fixed to the inner end of the inner shaft (4) protruding from the cylindrical outer shaft (3) to the inside of the fixed wall (1), whereas the fixed wall (1 ) The inner shaft input lever (8) is fitted on the outer end of the inner shaft (4) protruding outward from the outer shaft so as not to be relatively rotatable.
Of the outer shaft output lever (5) and the inner shaft output lever (7), one of the levers (5) and (7) serves as a speed adjustment output lever from the low speed rotation position (45) to the high speed rotation position. The other lever (7) and (5) are configured to be capable of reciprocatingly swinging to (46), while the other lever (7) and (5) are used as an engine stop output lever to release the stop device (11) for stopping the engine of the governor device (9). It is configured to be operable from the position (12) to the stop operation position (13)
A governor spring (10) of a governor device (9) provided inside the fixed wall (1) is engaged with the output lever for speed adjustment,
Correspondingly, one of the outer shaft input lever (6) and the inner shaft input lever (8), one of the levers (6) and (8) is a speed adjusting input lever, The other levers (8) and (6) are configured as engine stop input levers so that the input levers (6) and (8) can be operated.
In the pivoting device on the same axis center of the speed adjustment lever and the engine stop lever of the diesel engine,
The inner shaft input lever (8) is externally fitted to the inner shaft (4) so as not to rotate relative to the inner shaft (4), and approaches the inner shaft output lever (7) with a double nut (14). It is configured so that it can be pushed to the side and adjusted.
By adjusting the pushing of the double nut (14), the distance between the inner shaft input lever (8) and the inner shaft output lever (7) is shortened via the inner shaft (4). The input lever (8) presses the outer shaft input lever (6) against the bearing boss (2), while the inner shaft output lever (7) turns the outer shaft output lever (5) into the bearing boss (2). By pressing, the outer shaft input lever (6) and the outer shaft output lever (5) are frictionally fixed to the bearing boss (2), and the outer shaft input lever (6) and the cylindrical outer The inner shaft input lever (8) and the inner shaft output lever (7) are frictionally fixed to the shaft (3).
The speed adjusting lever and the engine stop lever of the diesel engine are characterized by the fact that they are pivotally supported on the same axis. In the pivoting device on the same axial center of the speed adjusting lever and the engine stop lever of the diesel engine according to claim 1,
The outer shaft output lever (5) and the outer shaft input lever (6) are configured to be compressed by the outer shaft return spring (15) from the operation position (46) side to the return position (45) side,
The inner shaft output lever (7) and the inner shaft input lever (8) are configured to be elastically pressed from the operation position (13) side to the return position (12) side by an inner shaft return spring (16).
The speed adjusting lever and the engine stop lever of the diesel engine are characterized by the fact that they are pivotally supported on the same axis. In the pivoting device on the same axial center of the speed adjusting lever and the engine stop lever of the diesel engine according to claim 2,
The outer shaft output lever (5), the outer shaft input lever (6), the outer shaft return spring (15), the return position (45), and the operation position (46) are respectively output to the speed adjustment output lever (5 ) ・ Speed adjustment input lever (6) ・ Speed adjustment lever return spring (15) ・ Low-speed rotation position (45) ・ High-speed rotation position (46)
The inner shaft output lever (7), the inner shaft input lever (8), the inner shaft return spring (16), the return position (12), and the operation position (13) are respectively connected to an engine stop output lever (7). )-Engine stop input lever (8)-Engine stop lever return spring (16)-Stop release position (12)-Stop operation position (13)
The spring base end portion (17) of the speed adjustment lever return spring (15) is locked to the fixed wall (1), and the spring free end portion (18) has a speed adjustment input lever (6) and a speed adjustment. Engage with one lever with the output lever (5)
A spring base end portion (19) of the engine stop lever return spring (16) is engaged with one of the speed adjustment output lever (5) and the speed adjustment input lever (6), and the spring The free end (20) is configured to engage with one of the engine stop output lever (7) and the engine stop input lever (8).
The speed adjusting lever and the engine stop lever of the diesel engine are characterized by the fact that they are pivotally supported on the same axis. In the pivotal support device on the same axial center of the speed adjusting lever and the engine stop lever of the diesel engine according to claim 1, 2 or 3,
The outer periphery of the inner shaft (4) at a position that fits into the outer shaft outer end side portion (3a) of the cylindrical outer shaft (3) protruding from the bearing boss (2) to the outer space of the fixed wall (1). On the surface portion, the rear side relief groove (21), the O-ring groove (22), and the outer side relief groove (23) are successively formed in order from the side closer to the bearing boss (2) to the side farther.
An O-ring (24) is inserted between the O-ring groove (22) and the outer shaft outer end side portion (3a), and the outer end portion of the outer relief circumferential groove (23) is connected to the outer shaft outer end side portion. The outer relief gap (23A) between the outer relief circumferential groove (23) and the outer shaft outer end side portion (3a) is positioned outside the outer end face of (3a). 21) and a clearance larger than the rear clearance gap (21A) between the outer shaft outer end side part (3a),
The speed adjusting lever and the engine stop lever of the diesel engine are characterized by the fact that they are pivotally supported on the same axis. In the pivoting device on the same axial center of the speed adjusting lever and the engine stop lever of the diesel engine according to claim 4,
The shaft centers of the bearing boss (2), cylindrical outer shaft (3) and inner shaft (4) are set up and down, and the speed adjusting input lever (6) and the engine stopping input lever (8) are Located above the fixed wall (1)
The outer part (3a) on the outer end of the cylindrical outer shaft (3) protrudes upward from the input lever (6) for speed adjustment and covers the outer periphery of the outer end (3a) of the outer shaft. The cylinder portion (26) is fixedly extended downward from the engine stop input lever (8) toward the speed adjustment input lever (6) side, and the lower end surface of the waterproof cylinder portion (26) is input to the outer shaft. Touching the lever (6),
The speed adjusting lever and the engine stop lever of the diesel engine are characterized by the fact that they are pivotally supported on the same axis. In the pivotal support device on the same axial center of the speed adjusting lever and the engine stop lever of the diesel engine according to claim 5,
A sealing seat surface (27) is formed at the back of the cylindrical hole of the waterproof cylinder portion (26) fixed to the lower portion of the inner shaft input lever (8), and the sealing seat surface (27) And an O-ring (28) inserted between the cylindrical outer shaft (3) and the upper end surface of the outer shaft outer end side portion (3a).
The speed adjusting lever and the engine stop lever of the diesel engine are characterized by the fact that they are pivotally supported on the same axis.

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