JPH11247671A - Electronic hydraulic governor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate such failures that there is a fear of erroneous operation in an electronic hydraulic governor by operating an erroneous operation of an actuator by inertia force in the case where a working apparatus and a marine vessel are rapidly advanced or rapidly stopped, and an engine is stopped without operating the electronic hydraulic governor in the case where an abnormal condition and a trouble are generated in an electric system, in a conventional electronic hydraulic governor. SOLUTION: A mechanical spool valve 5 which is mechanically controlled is arranged, a switching valve 15 is arranged so as to selectively control whether increase/decrease in a fuel injection rate is controlled by an electronic spool valve 2 or it is controlled by the mechanical spool valve 5. An actuator (an electromagnetic solenoid 14) for controlling an operation of the electronic spool valve 2 is arranged so as to set operating directions of the electronic spool valve 2 and the actuator 14 make a right angle with a horizontal direction and an advance direction of a mounted material on which the electronic hydraulic governor 1 is mounted.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a configuration of an electro-hydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve.

[0002]

2. Description of the Related Art There has been known an electrohydraulic governor which operates a piston by controlling a spool valve by electronic means such as an electromagnetic solenoid and adjusts a fuel injection amount of a fuel injection pump by the operation of the piston. I have. The electrohydraulic governor is mounted on a working machine diesel engine, marine diesel engine, or the like.

[0003]

However, since actuators such as electromagnetic solenoids for controlling the spool valve are arranged so that the operating direction is the traveling direction of the work implement or the boat, or the vertical direction, the work is Aircraft and ships suddenly start,
When the vehicle suddenly stops, or when the ship collides with a large wave and the hull is suddenly lifted upward, the actuator is actuated by inertial force and the electro-hydraulic governor may malfunction. Further, since the electro-hydraulic governor is controlled by electronic means, if an abnormality or failure occurs in the working machine or the electric system of the ship, the electro-hydraulic governor cannot be operated and the engine stops. It will be.

[0004]

The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described. That is, in the electrohydraulic governor which increases and decreases the fuel injection amount by using an electronically controlled electronic spool valve, a mechanically controlled mechanical spool valve is attached to the electronic hydraulic governor, and the increase and decrease of the fuel injection amount is controlled by an electronic system. A switching valve for selectively switching between control by a spool valve and control by a mechanical spool valve is provided.

According to a second aspect of the present invention, there is provided an electro-hydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve, and an electronic spool valve and an actuator for controlling the operation of the electronic spool valve. The operation direction of the electronic spool valve and the actuator is horizontal,
Further, the electrohydraulic governor is disposed so as to be perpendicular to the traveling direction of the object on which the electrohydraulic governor is mounted.

According to a third aspect of the present invention, there is provided an electrohydraulic governor for increasing or decreasing the fuel injection amount by using an electronically controlled electronic spool valve, wherein a mechanically controlled mechanical spool valve is provided to increase or decrease the fuel injection amount. And a switching valve for selectively switching between control by an electronic spool valve and control by a mechanical spool valve, and the switching valve is formed in the electronic spool valve.

According to a fourth aspect of the present invention, there is provided an electro-hydraulic governor for increasing or decreasing the fuel injection amount by using an electronically controlled electronic spool valve, wherein a mechanically controlled mechanical spool valve is provided to increase or decrease the fuel injection amount. By providing a switching valve for selectively switching between controlling by an electronic spool valve or controlling by a mechanical spool valve, the compensator mechanism operates on both the electronic spool valve and the mechanical spool valve. is there.

According to a fifth aspect of the present invention, there is provided an electrohydraulic governor for increasing / decreasing a fuel injection amount using an electronically controlled electronic spool valve, wherein a separate case in which an electronic control unit for controlling the electrohydraulic governor is built in. Is mounted on the governor main body, the lead wires of the electronic control unit are collectively pulled out from the upper surface of the separate case, and the gap between the lead wire and the upper surface of the separate case is sealed by a sealing member. That is, an air breather for communicating the internal space with the outside is mounted on the governor body upper surface.

According to a sixth aspect of the present invention, there is provided an electro-hydraulic governor for increasing / decreasing a fuel injection amount by using an electronically controlled electronic spool valve, wherein a separate case in which an electronic control unit for controlling the electro-hydraulic governor is incorporated. Is mounted on one surface of the governor main body, a temperature sensor is mounted on a portion of the governor main body opposite to the separate case mounting surface, and the temperature sensor is disposed near the electronic spool valve.

According to a seventh aspect of the present invention, in the electro-hydraulic governor for increasing or decreasing the fuel injection amount by using an electronically controlled electronic spool valve, a mechanically controlled mechanical spool valve is provided to increase or decrease the fuel injection amount. Is provided by a switching valve for selectively switching between control by an electronic spool valve and control by a mechanical spool valve.When control is performed by a mechanical spool valve, control is performed by an electronic spool valve. This is to control so as not to exceed the output limit range.

[0011]

Next, an embodiment of the present invention will be described. FIG. 1 is a block diagram showing an electrohydraulic governor of the present invention, and FIG. 2 is an electronic spool valve of the electrohydraulic governor.
A perspective view showing a mechanical spool valve, a power cylinder, and an oil passage between the switching valve, FIG. 3 is a side sectional view showing a first embodiment of the electrohydraulic governor, FIG.
FIG. 5 is a side sectional view showing the configuration of an electronic spool valve having a switching valve during electronic control. FIG. 6 is a side sectional view showing the configuration of an electronic spool valve having a switching valve during mechanical control. 8 is a plan sectional view showing a second embodiment of the electro-hydraulic governor, FIG. 8 is a sectional side view showing the same, FIG. 9 is a sectional side view showing a sleeve position fixing mechanism, and FIG. 10 is a sectional side view showing another embodiment. FIG. 11 is a diagram showing a change in displacement of a power piston when the engine speed is rapidly increased,
FIG. 12 is a plan sectional view showing a third embodiment of the electro-hydraulic governor, FIG. 13 is a side sectional view of the same, and FIG. 14 is an electronic spool valve of a switching valve having an internal passage formed in a substantially T-shape in side view. FIG. 15 is a side cross-sectional view showing the communication portion of the switching valve with the electronic spool valve when the mechanical spool valve is in communication with the power piston.
FIG. 16 is a side sectional view showing a communication portion between the mechanical spool valve and the power piston of the switching valve when the mechanical spool valve is in communication with the power piston. FIG. 17 is a sectional view of a compensator communication hole in the electronic spool valve. FIG. 18 is a side sectional view showing an example in which an aperture circuit is formed instead, FIG. 18 is a view showing a relationship between a lift amount of a power piston and a lift amount of a position sensor, and FIG. FIG. 20 is a side sectional view showing a seal member, FIG. 21 is a side sectional view showing a pressure regulating valve provided with a filter on a suction side and a discharge side, and FIG. 22 is an engine (engine) during mechanical control and electronic control. FIG. 4 is a diagram showing a relationship between a rotation speed and an angle of a terminal shaft (output shaft) of the electrohydraulic governor.

The mechanism of the electro-hydraulic governor of the present invention will be described. 1 and 2, the electro-hydraulic governor 1 is attached to a diesel engine such as a work machine or a ship, and includes a gear pump 12, an electronic spool valve 2, a mechanical spool valve 5,
And a power piston 8 and the like.

The gear pump 12 is connected to a gear shaft 11. The rotation of the crankshaft in the engine is transmitted to the gear shaft 11, and the rotation of the gear shaft 11 drives the gear pump 12. The gear pump 12
The hydraulic oil is sucked through the pressure regulating valve 13 and the high-pressure hydraulic oil is pressure-fed to the mechanical pilot valve 6 through the high-pressure hydraulic oil passage 21. The high-pressure hydraulic oil pumped by the gear pump 12 is regulated to a constant pressure by a pressure regulating valve 13. The high-pressure hydraulic oil is also fed to the upper part of the power piston 8 through the high-pressure hydraulic oil passage 21 to urge the power piston 8 downward.

The electronic spool valve 2 is a pilot valve 3
A sleeve 4 is slidably fitted to the outer peripheral portion of the pilot valve 3.
Is pumping hydraulic oil. The pilot valve 3 is configured to be biased leftward in the axial direction by a spring 16 and moved rightward in the axial direction by the operation of an electromagnetic solenoid 14 which is an actuator. A pilot port 4 a is formed in the sleeve 4. In FIG. 1, the pilot port 4 a is closed by a valve land 3 a formed substantially in the center of the pilot valve 3. The pilot port 4a communicates with the lower part of the power piston 8 through the communication passage 33 via the switching valve 15.

In the state shown in FIG. 1, the power piston 8 is stopped at a fixed position, and when the valve land 3a moves rightward due to the operation of the electromagnetic solenoid 14, the high pressure working oil passage 21 and the pilot port 4a communicate with each other. Thus, the high-pressure hydraulic oil is pumped to the lower part of the power piston 8.
When high-pressure hydraulic oil is pumped to the lower part of the power piston 8,
Since the pressure receiving area of the lower surface 8b of the power piston 8 is configured to be larger than the pressure receiving area of the upper surface 8a, the power piston 8 moves upward. When the power piston 8 is raised, the terminal shaft 17 connected to the power piston 8 and the terminal arm 35 is rotated. Conversely, when the valve land 3a moves leftward due to the operation of the electromagnetic solenoid 14 and the urging force of the spring 16, the pilot port 4a and the drain port 4b communicate with each other, and the hydraulic oil below the power piston 8 returns to the oil reservoir. Then, the power piston 8 moves downward, and the terminal shaft 17 is rotated in a direction opposite to the case where the power piston 8 moves upward.

The electrohydraulic governor 1 has a position sensor 36 for detecting the amount of rotation of the terminal shaft 17 and detecting the amount of displacement of the power piston 8, which is rotated by the vertical movement of the power piston 8. It is arranged. Further, the terminal arm 35 vertically rotates around the terminal shaft 17 by the vertical movement of the power piston 8, but with the vertical rotation of the terminal arm 35, the floating lever 37 rotates vertically about the fulcrum 37a. By moving the speeder spring 10, the urging force of the speeder spring 10 with respect to the mechanical mechanical pilot valve 6 is changed. On the other hand, the mechanical spool valve 5 is configured by slidably fitting a mechanical sleeve 7 to an outer peripheral portion of a mechanical pilot valve 6.
Gear pump 1 composed of 2a and driven gear 12b
Two driven gears 12 b are formed integrally with the lower end of the mechanical sleeve 7. A flyweight 9 is integrally rotatably attached to the upper end of the mechanical sleeve 7, and the mechanical pilot valve 6 is configured to move up and down by centrifugal force accompanying the rotation of the flyweight 9. The pilot valve 6 is urged downward by a speeder spring 10.

Hydraulic oil is fed to the mechanical pilot valve 6 from the high-pressure hydraulic oil passage 21, and a mechanical pilot port 7a is formed in the mechanical sleeve 7. In FIG. 1, the mechanical pilot port 7a is a mechanical pilot port. The pilot valve 6 is closed by a valve land 6a formed substantially at the center. The mechanical pilot port 7a can communicate with the lower part of the power piston 8 through the communication passage 33 and the like by switching the switching valve 15. Then, the switching valve 15 is switched to switch the mechanical pilot port 7a.
When the mechanical piston port 7a is closed by the valve land 6a as shown in FIG. 1, the power piston 8 is stopped at a fixed position when the power piston 8 is communicated with the lower part of the power piston 8.

The mechanical pilot valve 6 is
It moves up and down according to the rotation speed of the mechanical sleeve 7 driven to rotate by the gear shaft 11 and the urging force of the speeder spring 10. When the mechanical pilot valve 6 moves downward from the vertical position in FIG. 1, the high-pressure hydraulic oil passage 21 communicates with the mechanical pilot port 7 a, and the high-pressure hydraulic oil is pumped to the lower part of the power piston 8. Becomes When the high-pressure hydraulic oil is pumped to the lower part of the power piston 8, as described above, the pressure receiving area of the lower surface 8b of the power piston 8 is configured to be larger than the pressure receiving area of the upper surface 8a. Then, the terminal shaft 17 is rotated.
Conversely, when the mechanical pilot valve 6 moves upward, the mechanical pilot port 7a and the drain port 7
b, the hydraulic oil below the power piston 8 is returned to the oil reservoir, the power piston 8 moves downward, and the terminal shaft 17 moves in the opposite direction to the case where the power piston 8 moves upward. Is rotated.

When the power piston 8 moves upward, the terminal shaft 17 rotates in a direction to increase the fuel injection amount of the fuel injection pump, and when the power piston 8 moves downward, the terminal shaft 17 moves downward. , Terminal shaft 1
Numeral 7 is configured to rotate in a direction to decrease the fuel injection amount of the fuel injection pump. By operating the control lever 31 to rotate the speed control shaft 30, the urging force of the speeder spring 10 against the mechanical pilot valve 6 is changed, and the power piston 8 is moved up and down to increase or decrease the fuel injection amount. It is configured to be able to.

As described above, in the present electro-hydraulic governor 1, the power piston 8 is operated by controlling the electronic spool valve 2 by the electromagnetic solenoid 14, and the fuel injection of the fuel injection pump is performed by the operation of the power piston 8. By changing the amount and switching the switching valve 15, the power piston 8 is operated by operating the mechanical spool valve 5, so that the fuel injection amount of the fuel injection pump can be increased or decreased.

The electro-hydraulic governor 1 is provided with a compensator mechanism, and the compensator mechanism is configured as follows. That is, the power piston 8
Has a push rod 22 slidably fitted therein.
An upper spring 24 and a lower spring 25 are fitted to the push rod 22, and a set load is applied so that a load is applied to the push rod 22 when the push rod 22 moves upward or downward with respect to the power piston 8. I have. A compensating piston 23 is formed at the lower end of the push rod 22, and a compensator chamber 26 is provided above the compensating piston 23.
Is configured.

For example, when the power piston 8 moves downward in the fuel decreasing direction, at the start of the movement, the power piston 8, the push rod 22, and the compensating piston 23 integrally move downward.
As a result, a negative pressure is generated in the compensator chamber, and when the negative pressure falls below a certain value, the set load of the upper spring 24 is overcome, and the upper spring 24 is deflected. The movement amount of the piston 23 relatively decreases.

Here, the compensator chamber 26 communicates with a pilot valve lower chamber 27 formed below the mechanical pilot valve 6 and a pilot valve right chamber 28 formed to the right of the pilot valve 3. The pilot valve lower chamber 27 and the pilot valve right chamber 28 are also in a negative pressure state. Therefore, for example, when the electronic spool valve 2 is in communication with the power piston 8 by the switching valve 15, the electromagnetic solenoid 1
By the actuation of 4 and the urging force of the spring 16, a force in the direction in which the pilot valve 3 that has moved to the left moves to the right acts, and acts to close the pilot port 4a that has been opened by the valve land 3a. . When the mechanical spool valve 5 is in communication with the power piston 8 by the switching valve 15, the pilot valve lower chamber 2
7 acts to move the mechanical pilot valve 6 downward against the centrifugal force of the flyweight 9,
The mechanical pilot port 7a, which has been opened once, is closed by the valve land 6a.

On the other hand, when the power piston 8 moves upward, the inside of the pilot valve right chamber 28 and the pilot valve lower chamber 27 are in a positive pressure state, and the pilot valve 3 is moved to the left to open the pilot port 4a. The force acting to close or the mechanical pilot valve 6
Is moved upward to act to close the mechanical pilot port 7a.

Thus, the operation of the electromagnetic solenoid 14
Alternatively, since the operation speed of the power piston 8 with respect to the change in the rotation speed of the flyweight 9 can be reduced to some extent, hunting during operation of the electrohydraulic governor 1 can be prevented. Thus, a compensator mechanism for preventing hunting of the electro-hydraulic governor 1 is configured,
The operation of the compensator mechanism operates on both the electronic spool valve 2 and the mechanical spool valve 5. still,
When the pilot valve right chamber 28 and the pilot valve lower chamber 27 are in a negative pressure state, oil gradually flows from the oil reservoir from the needle valve 29 and returns to the atmospheric pressure state after a certain time. When the compensator effect disappears and the pilot valve right chamber 28 and the pilot valve lower chamber 27 are in a positive pressure state, the oil gradually flows out of the needle valve 29 to the oil reservoir and after a certain time, It is configured to return to the atmospheric pressure state and the compensator effect disappears.

FIGS. 3 and 4 show a switching valve 15 on the outer periphery of the sleeve 4 of the electronic spool valve 2 in the electro-hydraulic governor 1.
Is formed. That is, the electronic spool valve 2
Controls the operation of the power piston 8 and operates the switching lever 32 to move the position of the sleeve 4 so that the operation of the power piston 8 is controlled by the electronic spool valve 2.
And control by the mechanical spool valve 2 is performed.

The configuration of switching between electronic control and mechanical control by the switching valve 15 formed on the outer periphery of the sleeve 4 of the electronic spool valve 2 will be described with reference to FIGS. First, FIG. 5 shows a state where the sleeve 4 is moved to the left and the power piston 8 is electronically controlled by the electronic spool valve 2. High-pressure hydraulic oil is supplied to the pilot valve 3 of the electronic spool valve 2 from the high-pressure hydraulic oil passage 21, and the pilot port 4 a of the sleeve 4 communicates with the lower part of the power piston 8 through the communication passage 33. The position of the valve land 3a of the pilot valve 3 is moved left and right by the electromagnetic solenoid 14 to control the flow of hydraulic oil to the lower part of the power piston 8, thereby controlling the operation of the power piston 8. In this case, the mechanical pilot port 7 a of the mechanical spool valve 5 communicates with a portion of the switching valve 15 formed on the outer periphery of the sleeve 4 by the communication passage 34, but the switching valve 15 communicates with the power piston 8. No mechanical spool valve 5
Does not control the power piston 8.

On the other hand, in FIG. 6, the sleeve 4 is moved rightward, and the power piston 8 is moved to the mechanical spool valve 5.
2 shows a state in which the apparatus is mechanically controlled. The pilot valve 3 of the electronic spool valve 2 has a high-pressure hydraulic oil passage 2
Although high-pressure hydraulic oil is supplied from 1, the pilot port 4 a of the sleeve 4 is not communicated with the power piston 8, and the hydraulic oil has a dead end up to the pilot port 4 a. The mechanical pilot port 7 a of the mechanical spool valve 5 communicates with the switching valve 15 through a communication passage 34, and the switching valve 15 communicates with the power piston 8 through a communication passage 33. Thereby, the position of the valve land 6a of the mechanical pilot valve 6 in the mechanical spool valve 5 is moved up and down to control the flow of hydraulic oil to the lower part of the power piston 8,
The operation of the power piston 8 can be controlled. In this case, the pilot port 4a of the electronic spool valve 2 reaches a dead end and is not in communication with the power piston 8, so that the control of the power piston 8 by the electronic spool valve 2 is not performed.

As described above, by operating the switching lever 32 in FIG. 3 to move the electronic spool valve 2 to the left or right, the operation of the power piston 8 is controlled by electronic control or by mechanical control. It is configured to switch whether to perform.

In the electro-hydraulic governor 1 shown in FIGS. 3 and 4, the electronic spool valve 2 and the electromagnetic solenoid 14, which is an actuator, are arranged so that the operation directions are horizontal. When the governor 1 is mounted on a load such as a work implement or a ship, the electronic spool valve 2 and the electromagnetic solenoid 14 are arranged so that the operating directions are perpendicular to the direction of travel of the load.

The shaft 36a of the position sensor 36 for detecting the amount of vertical movement of the power piston 8 is connected to the terminal shaft 17 by a connecting shaft 39. The connecting portion between the shaft portion 36a and the terminal shaft 17 includes:
Each is rotatably connected by a pin 38.
The lead wires 40 for transmitting signals from a power supply and a controller to electronic devices such as the position sensor 36 and the electromagnetic solenoid 14 are collectively taken out of the electrohydraulic governor 1 at one place.

The electrohydraulic governor 1 may be configured as shown in FIGS. That is, the electronic spool valve 52 of the electrohydraulic governor 51 shown in FIGS. 7 and 8 is configured by slidably fitting a sleeve 54 around the outer periphery of a pilot valve 53. The operation of the power piston 8 is controlled similarly to the electronic spool valve 2, and the mechanical spool valve 55 of the electrohydraulic governor 51 controls the operation of the power piston 8 similarly to the mechanical spool valve 5 of the electrohydraulic governor 1. Is configured. The sleeve 54 of the electronic spool valve 52 and the sleeve 68 of the mechanical spool valve 55 have a compensator communication hole 67 and a compensator communication hole 6 respectively.
8 are provided, and the compensator communication holes 67.6 are provided.
8, both the lower pilot valve chamber 27 and the right pilot valve chamber 28 shown in FIG. 1 communicate with the compensator chamber 26.

The sleeve 5 of the electronic spool valve 52
A switching valve 15 is formed in 4 similarly to the case of the electronic spool valve 2, and switching between the electronic spool valve 52 and the mechanical spool valve 55 is performed by a switching lever 61. The switching lever 61 and a spring fork 63 rotatably fitted to the control shaft 30.
Are connected by a switching link 67, and the switching link 67 rotates with the rotation of the switching lever 61. A long hole 63a is formed in the circumferential direction on the upper surface of the spring fork 63,
A pin 64 protruding from the control shaft 30 is movably fitted into the long hole 63a.

In the electro-hydraulic governor 51,
When an accelerator such as a work machine or a ship on which an engine provided with the electro-hydraulic governor 51 is mounted is operated, the control shaft 30 is rotated in conjunction with the operation of the accelerator. Accordingly, when the power cylinder 8 is switched to be controlled by the electronic spool valve 52, the spring fork 63 does not rotate even if the control shaft 30 rotates. That is, as described above, the spring fork 63 is rotatably fitted to the control shaft 30 and projects from the control shaft 30 when the power cylinder 8 is switched to be controlled by the electronic spool valve 52. Pin 64 is a spring fork 6
3 is movable in the long hole 63a, so that even if the control shaft 30 is rotated, the pin 64 remains in the long hole 63a.
The spring fork 63 does not rotate merely by moving inside.

On the other hand, when the switching lever 61 is switched so that the power cylinder 8 is controlled by the mechanical spool valve 55, the upper surface of the spring fork 63 rotates in the direction of the switching lever 61 via the switching link 62. I do. When the pin 64 reaches the end of the long hole 63a, the spring fork 63 is urged downward in FIG. The stopper 69, which has prevented movement in the urging direction, comes off, and the pin 64 fits into a locking hole connected to the elongated hole 63a. As a result, the pin 64 is fixed in the rotation direction with respect to the spring fork 63, and the control shaft 30 and the spring fork 63 rotate integrally. Accordingly, when the control shaft 30 is rotated by the accelerator operation, the spring fork 63 is integrally rotated to expand and contract the speeder spring 10, so that the mechanical spool valve 55 is interlocked with this rotating operation. .

As described above, when the power cylinder 8 is controlled by the electronic spool valve 52, the accelerator operation is not interlocked with the mechanical spool valve 55, and the power cylinder 8 is controlled by the mechanical spool valve 55. In this case, the accelerator operation is interlocked with the mechanical spool valve 55 when switching is performed so as to be controlled.

As shown in FIG. 8, a concave portion 54b is formed at the lower part of the outer periphery of the sleeve 54 of the electronic spool valve 52, and is urged in the direction of the sleeve 54 by the spring 71 below the outer periphery of the sleeve 54. When the ball member 70 is provided and the power cylinder 8 is controlled by the mechanical spool valve 55 by switching the switching lever 61, the ball member 70 fits into the recess 54b. When the switching lever 61 is switched to the mechanical control side, the sleeve 54 moves to the left, and the ball member 70 is pushed out of the concave portion 54b against the urging force of the spring 71. In this way, the configuration is such that the position of the sleeve 54 is fixed when switching to mechanical control is performed by fitting the ball member 70 into the concave portion 54b of the sleeve 54.

The position fixing mechanism of the sleeve 54 is shown in FIG.
It can also be configured as shown in FIG. That is, the electronic spool valve 5
A concave member 54c is formed in the upper part of the outer periphery of the sleeve 54, and a ball member 72 urged in the direction of the sleeve 54 by a spring 73 is disposed above the outer periphery of the sleeve 54. When controlled by 55, the ball member 72 is configured to fit into the recess 54c. The ball member 7
2 is inserted from above into a through hole 51b formed in an upper portion of the sleeve 54 in a casing 51a, which is a governor main body of the electro-hydraulic governor 51, and a spring 73 is disposed above the ball member 72, from above. Through hole 51
The fixing member 74 is threadedly fitted to the “b”. That is, the spring 73 is interposed between the fixed member 74 detachably screwed to the casing 51a and the ball member 72 to urge the ball member 72 toward the concave portion 54c of the sleeve 54,
The ball member 72 is fitted in the concave portion 54c. Since the fixing member 74 is detachably screwed to the casing 51a, by removing the fixing member 74, the spring 73 is replaced to change the urging force,
The ball member 72 can be removed.

Further, as shown in FIG.
A switching spring 75 may be provided on the left side of 4 to bias the sleeve 54 to the right by the switching spring 75. As a result, when the ball member 72 is pulled out of the recess 54c by operating the switching lever 61, the sleeve 54 urged by the switching spring 75 automatically moves to a position where electronic control is performed.

As shown in FIG. 7, a pilot port 54 of an electronic spool valve 52 constituting a high-pressure control circuit is provided.
The accumulator 76 is attached to a. Thus, when the accelerator is rapidly accelerated or decelerated, the responsiveness of the operating oil pressure from the electronic spool valve 52 to the power piston 8 can be improved, and the generation of pulsating pressure can be prevented. For example, as shown in FIG. 11, in a graph 101 showing a change in displacement of the power piston 8 when the rotation speed of the engine is rapidly increased when the accumulator 76 is not attached to the high-pressure control circuit, Rises, the displacement of the power piston 8 decreases, but the displacement after the decrease fluctuates and is not stable. On the other hand, in the graph 102 in the case where the accumulator 76 is attached to the high-pressure control circuit, the displacement of the power piston 8 after the rotation speed increases is constant and stable. in this way,
By attaching the accumulator 76 to the high-pressure control circuit, it is possible to prevent the generation of pulsating pressure and to stabilize the behavior of the power piston 8.

In the electro-hydraulic governor 51, the electro-hydraulic governor 5 such as the electromagnetic solenoid 14 and the position sensor 36 is used.
1 is built in a separate case 51b, and the separate case 51b is mounted on a position side surface of a casing 51a which is a governor main body. Then, the electromagnetic solenoid 14 and the position sensor 36 in the electronic control unit are used.
Lead wires 40 are collectively drawn upward from the upper surface located at the uppermost portion of the separate case 51b.
This prevents the hydraulic oil in the casing 51a from leaking to parts of the electronic device such as the electromagnetic solenoid 14 and the position sensor 36. Even if the operating oil leaks to the separate case 51b, the lead wires of these electronic devices may be prevented. Since 40 is pulled out upward from the upper surface located at the top of the separate case 51b, oil does not leak outside.

The switching valve for switching between the electronic control and the mechanical control may be configured as a switching valve 83 of the electrohydraulic governor 81 shown in FIGS. The electronic spool valve 52 of the electro-hydraulic governor 81 is provided horizontally in the horizontal direction, and the mechanical spool valve 55 is provided upright in the vertical direction. The switching valve 83 is disposed horizontally and orthogonally to the electronic spool valve 52 in a plan view. Electro-hydraulic governor 81 in FIGS. 12 to 14
Are switched to be electronically controlled by the switching valve 83, the electronic spool valve 52 and the power piston 8 are communicated, and the mechanical spool valve 55 and the power piston 8 are not communicated.

A passage 83a is formed in the switching valve 83. In this state, the passage 83a and the pilot port 54a of the electronic spool valve 52 are communicated by an electronic control pilot port side communication port 83b. Passage 8
The power piston 3a is communicated with the power piston 8 through the communication passage 33 by the power piston side communication port 83c for electronic control. As a result, the electronic spool valve 52 and the power piston 8 communicate with each other, and the electronic hydraulic governor 81 is electronically controlled.

The switching valve 83 is connected to an operating portion 82a of a switching actuator 82 which is constituted by a motor, a solenoid, or the like and is electrically driven. The operation of the switching actuator 82 causes the switching valve 83 to rotate. It is configured to work. Then, from this state, the electro-hydraulic governor 81
Is switched to a state in which is controlled mechanically, the switching actuator 82 is operated, and the switching valve 83 is rotated by approximately 90 ° so as to be in the state shown in FIGS.
15 and 16, the electrohydraulic governor 81 is switched to a state in which the electrohydraulic governor 81 is mechanically controlled by the switching valve 83, and the passage 83a of the switching valve 83, the pilot port 54a of the electronic spool valve 52, and the passage 83a And the electronic control power piston side communication port 83c are not communicated.

On the other hand, the pilot port 57a of the mechanical pilot valve 57 in the mechanical spool valve 55
And the passage 83a are communicated with each other through the communication passage 34 by the mechanical control pilot port side communication opening 83d, and the passage 83a and the power piston 8 are connected to the communication passage 33.
Through the power piston side communication port 83e for machine control. Thereby, the mechanical spool valve 55
And the power piston 8 are communicated with each other.
Are in a state of being mechanically controlled.

As described above, the switching state of the electrohydraulic governor 81 can be switched between electronic control and mechanical control by rotating the switching valve 83 using the switching actuator 82 that is electrically driven. It is composed. 13 and 16 in the switching valve 83.
As shown in the figure, a passage 83a has an electronic control power piston side communication port 83c, a machine control pilot port side communication port 83d, and a machine control power piston side communication port 83.
When e is formed in a substantially T-shape and the switching valve 83 is rotated by about 90 °, electronic control and mechanical control are switched. Further, since the switching valve 83 is rotated by the switching actuator 82 which is electrically driven, for example, when the electrohydraulic governor 81 is electronically controlled, a failure occurs in the electronic control portion and the When control becomes impossible, the switching actuator 82 can be operated by detecting this defect electrically to automatically switch from electronic control to mechanical control.

The electro-hydraulic governor 1, the electro-hydraulic governor 5
1, and the compensator mechanism is configured in the electro-hydraulic governor 81 and the like as described above. In particular, in the electro-hydraulic governor 51 and the electro-hydraulic governor 81, the compensator communication hole 67 is formed in the electronic spool valve 52, Forming a compensator communication hole 68 in the mechanical spool valve 55,
The compensator communication holes 67 and 68 and the power piston 8
The lower compensator chamber 26 is in communication with the lower spool, and the compensator mechanism includes an electronic spool valve 52 and a mechanical spool valve 5.
5. Thus, the compensator mechanism operates in both cases where the electro-hydraulic governor 81 is electronically controlled and when the electro-hydraulic governor 81 is mechanically controlled, thereby preventing hunting during operation of the electro-hydraulic governors 51 and 81. .

For example, a throttle circuit 86 as shown in FIG. 17 is formed instead of the compensator communication hole 67 in the electronic spool valve 52 of the electrohydraulic governor 81, and the electronic spool valve 52 is formed by the throttle circuit 86. And the oil chamber 85 may be configured to communicate with each other. Accordingly, the hydraulic oil that flows in and out of the pilot valve right chamber 87 of the electro-hydraulic governor 81 has a function similar to that of the pilot valve right chamber 28 in FIG. Can be played. It goes without saying that the electrohydraulic governor 51 and the like can be similarly configured.

In the electro-hydraulic governor 81 shown in FIG. 13, the detecting portion 36a of the position sensor 36 for detecting the amount of rotation of the terminal shaft 17 is connected to the terminal arm 35.
, And the amount of rotation of the terminal shaft 17 is detected by the vertical movement of the terminal arm 35. That is, when the power piston 8 moves up and down,
The terminal arm 35 is rotated up and down to rotate the terminal shaft 17. By contacting the detection part 36 a of the position sensor 36 with the upper side of the terminal arm 35, the amount of up and down movement of the contact part is transmitted to the position sensor 36. Thus, the rotation amount of the terminal shaft 17 is detected. Thereby, the amount of rotation of the terminal shaft 17 indicating the amount of displacement of the power piston 8 can be linearly extracted. The relationship between the lift amount of the power piston 8 and the lift amount of the position sensor detected as described above is such that the lift amount of the position sensor increases substantially linearly with the increase amount of the power piston lift amount as shown in FIG. doing.

In the electro-hydraulic governor 51 shown in FIG. 8, the lead wires 40 of the electromagnetic solenoid 14, the position sensor 36 and the like are pulled out upward from the upper surface of the separate case 51b. A seal member is interposed in the drawer portion of the device to prevent oil from leaking to the outside. That is, as shown in FIG.
The leading end 88a of the lead wire draw-out case 88 is fitted and fixed in the lead wire draw-out port 51c on the upper surface 1b. Each lead wire 40 passes through the inside of the lead wire draw-out case 88, and at the tip end portion 88 a of the lead wire draw-out case 88, a sealing member as shown in FIG. 89 are interposed. The seal member 89 is made of an elastic member such as rubber having oil resistance, and the lead wire 40 is passed through the through hole 89 a of the seal member 89. And the sealing member 8
The lead wire 40 and the lead wire 40 and the leading end portion 88a of the lead wire draw-out case 88 are in close contact with each other so as not to leak oil. In addition, the distal end portion 88a of the lead wire draw-out case 88 is also formed of a member that is in close contact with the lead wire draw-out port 51c of the separate case 51b, so that oil leakage from between the distal end portion 88a and the lead wire draw-out port 51c is prevented. Preventing.

Further, in the electro-hydraulic governor 51,
An air breather 90 that connects the oil chamber inside the casing 51a to the outside is attached from the upper surface of the casing 51a, and is adjusted so that the pressure in the oil chamber inside the casing 51a does not become too large. Prevents oil leaks. As described above, in the electro-hydraulic governor 51, since the oil leakage prevention mechanism is configured in both the casing 51a and the separate case 51b, it is possible to reliably prevent oil leakage from the electro-hydraulic governor 51 to the outside. You can.

As shown in FIG. 8, a separate case 51b in a casing 51a is provided on the electro-hydraulic governor 51.
And the mechanical spool valve 5
5, a temperature sensor 91 is attached near the mechanical spool valve 55 in the casing 51a.
It is configured to detect a nearby oil temperature. Position sensor 36 and electromagnetic solenoid 1 built in separate case 51b
Since the electronic devices such as 4 generate heat by operating, the oil temperature near these electronic devices increases with time. In order to avoid this change in oil temperature, the separate case 51b is located at a position away from the separate case 51b containing the electronic device.
The temperature sensor 91 is mounted on the side surface opposite to the mounting surface. As described above, the control accuracy of the electrohydraulic governor 51 is improved by detecting the oil temperature near the mechanical spool valve 55 while avoiding the influence of heat generated by the electronic device.

Further, as shown in FIG. 21, the electro-hydraulic governor 51 is provided with a high-pressure actuation pumped by a gear pump 12 driven by the rotation of a gear shaft 11, like the pressure regulating valve 13 in the electro-hydraulic governor 1 of FIG. A pressure regulating valve 92 for regulating oil to a constant pressure is provided. Gear pump 12
The hydraulic oil sucked into the gear pump 12 from the oil reservoir by the driving of the pump is sucked into the gear pump 12 through the pressure regulating valve 92, and a filter 9 is provided on the suction side 92 a of the pressure regulating valve 92.
3 is attached to prevent foreign matter in the hydraulic oil from entering the gear pump 12. The high-pressure hydraulic oil from the gear pump 12 is fed to the mechanical spool valve 55 and the like through the pressure regulating valve 92. The filter 94 is attached to the discharge side 92b of the pressure regulating valve 92 and the mechanical spool valve 55 and the like are attached. Foreign matter in the high-pressure hydraulic oil is prevented from entering inside. Since the control unit such as the mechanical spool valve 55 is more precise than the gear pump 12, and it is necessary to remove fine foreign matter, the filter 94 on the discharge side 92b is more suitable for the filter on the suction side 92a. The eyes are made finer than 93. Thus, the filters 93 and 94 are provided on both the suction side 92a and the discharge side 92b of the pressure regulating valve 92.
The gear pump 12 and the mechanical spool valve 55
And other control units are protected from failure due to foreign matter in the hydraulic oil. Note that the filter 93 is similarly provided on the electro-hydraulic governor 81.
-A pressure regulating valve 92 to which 94 is attached is provided.

In the electro-hydraulic governors 51 and 81, the number of rotations by the machine control is limited when the machine control is performed. FIG. 22 shows the engine (engine) rotational speeds during mechanical control and electronic control, and the electro-hydraulic governors 51.5.
8 shows the relationship between the angle of the terminal shaft 17 (output shaft) and the angle of the terminal shaft 17 (output shaft). As the angle of the terminal shaft 17 (output shaft) increases, the fuel injection amount increases. Then, as shown in FIG. 22, the mechanical control range of the mechanical spool valve 55 is set such that the rotational speed substantially equal to the rotational speed at the maximum rack position after torque rise by electronic control by the electronic spool valve 52 is the maximum rotational speed. The engine is operated so as not to exceed the torque rise range of the output map by electronic control during machine control.
That is, at the time of machine control, control is performed so as not to enter the output limit range 95 for electronic control shown in FIG. As a result, an excessive load is prevented from being applied to the engine, and the durability of the engine is ensured.

[0055]

As described above, the present invention has the following advantages. That is, as set forth in claim 1, a mechanically controlled mechanical spool valve is additionally provided, and a switching valve for selectively switching between increasing and decreasing the fuel injection amount by an electronic spool valve or by a mechanical spool valve. Therefore, for example, when the electronic hydraulic governor is electronically controlled by the electronic spool valve, when a failure occurs in the electronic control part and the electronic control can no longer be performed, the switching valve is used to control the electronic hydraulic governor. The control can be switched to be performed by a mechanical spool valve, and the stability and safety during engine operation can be improved.

According to a second aspect of the present invention, there is provided an electronic spool valve and an actuator for controlling the operation of the electronic spool valve, wherein the operation direction of the electronic spool valve and the actuator is horizontal and the electrohydraulic governor is provided. Are arranged at right angles to the traveling direction of the mounted object, for example, when the mounted object such as a work machine or ship suddenly starts or stops, or the ship collides with a large wave When the hull is suddenly lifted upward, the actuator and the electronic spool valve are activated by the inertial force, and it is possible to prevent the electrohydraulic governor from malfunctioning. Safety could be improved.

Further, as set forth in claim 3, a mechanically controlled mechanical spool valve is additionally provided to selectively switch between an electronic spool valve and a mechanical spool valve to increase or decrease the fuel injection amount. Since the switching valve is provided on the electronic spool valve, there is no need to provide a separate switching valve, so that the structure can be simplified and the cost can be reduced, and the failure of the electro-hydraulic governor can be reduced. The occurrence could be reduced.

Further, as set forth in claim 4, a mechanically controlled mechanical spool valve is additionally provided to selectively switch between an electronic spool valve and a mechanical spool valve to increase or decrease the fuel injection amount. And a compensator mechanism is configured to act on both the electronic spool valve and the mechanical spool valve, so that both when the electronic hydraulic governor is electronically controlled and when it is mechanically controlled. In such a case, the compensator mechanism was operated, and hunting during operation of the electrohydraulic governor could be prevented.

Further, a separate case containing an electronic control unit for controlling the electro-hydraulic governor is mounted on the governor body, and a lead wire of the electronic control unit is moved upward from the upper surface of the separate case. And pulled out together, sealing between the lead wire and the upper surface of the separate case with a seal member,
In addition, since the air breather that connects the space inside the governor main body and the outside is attached to the upper surface of the governor main body, it is possible to prevent both oil leakage from the governor main body and oil leakage from the separate case, and Oil leakage to the outside from the hydraulic governor was reliably prevented.

Further, a separate case containing an electronic control unit for controlling the electro-hydraulic governor is mounted on one surface of the governor main body, and the opposite side of the separate case mounting surface of the governor main body. Since the temperature sensor is attached to the part and the temperature sensor is arranged near the electronic spool valve, it is possible to detect the oil temperature near the mechanical spool valve, avoiding the influence of heat generated by the electronic control unit. Thus, the control accuracy of the electro-hydraulic governor can be improved.

Further, when the control is performed by the mechanical spool valve, the control is performed so as not to exceed the output limit range when the control is performed by the electronic spool valve. In addition, it was possible to prevent an excessive load from being applied to the engine, thereby ensuring the durability of the engine.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing an electro-hydraulic governor of the present invention.

FIG. 2 is a perspective view showing an oil path between an electronic spool valve, a mechanical spool valve, a power cylinder, and a switching valve in the same electro-hydraulic governor.

FIG. 3 is a side sectional view showing a first embodiment of the electrohydraulic governor.

FIG. 4 is a plan sectional view of the same.

FIG. 5 is a side sectional view showing a configuration of an electronic spool valve in which a switching valve is formed during electronic control.

FIG. 6 is a side sectional view showing a configuration of an electronic spool valve forming a switching valve during mechanical control.

FIG. 7 is a plan sectional view showing a second embodiment of the electrohydraulic governor.

FIG. 8 is a side sectional view of the same.

FIG. 9 is a side sectional view showing a position fixing mechanism of the sleeve.

FIG. 10 is a side sectional view showing another embodiment.

FIG. 11 is a diagram illustrating a change in displacement of a power piston when the engine speed is rapidly increased.

FIG. 12 is a plan sectional view showing a third embodiment of the electrohydraulic governor.

FIG. 13 is a side sectional view of the same.

FIG. 14 is a side cross-sectional view showing a portion of the switching valve in which an internal passage is formed in a substantially T-shape in side view and which communicates with an electronic spool valve.

FIG. 15 is a side sectional view showing a communication portion of the switching valve with the electronic spool valve when the mechanical spool valve is in communication with the power piston.

FIG. 16 is a side cross-sectional view showing a portion of the switching valve communicating with the mechanical spool valve and the power piston when the mechanical spool valve is in communication with the power piston.

FIG. 17 is a side sectional view showing an example in which a throttle circuit is formed instead of the compensator communication hole in the electronic spool valve.

FIG. 18 is a diagram showing a relationship between a power piston lift amount and a position sensor lift amount.

FIG. 19 is a side cross-sectional view showing the lead-out portion of the electronic device on the upper surface of the separate case.

FIG. 20 is a side sectional view showing a seal member.

FIG. 21 is a side sectional view showing a pressure regulating valve provided with a filter on a suction side and a discharge side.

FIG. 22 is a diagram illustrating a relationship between an engine (engine) rotation speed at the time of mechanical control and electronic control and an angle of a terminal shaft (output shaft) of the electro-hydraulic governor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Electro-hydraulic governor 2 Electronic spool valve 3 Pilot valve 4 Sleeve 4a Pilot port 5 Mechanical spool valve 6 Mechanical pilot valve 7 Mechanical sleeve 7a Mechanical pilot port 8 Power piston 9 Flyweight 10 Speeder spring 12 Gear pump 13 Pressure regulating valve 14 Electromagnetic solenoid (Actuator) 15 Switching valve 17 Terminal shaft 26 Compensator chamber 29 Needle valve 30 Speed control shaft 36 Position sensor 40 Lead wire 91 Temperature sensor 95 Output limit area

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tsuyoshi Tanimoto 1-32 Chaya-cho, Kita-ku, Osaka, Osaka Inside Yanmar Diesel Co., Ltd. (72) Inventor Shinobu Sakuma 1-32, Chaya-cho, Kita-ku, Osaka, Osaka Inside Yanmar Diesel Co., Ltd. (72) Inventor Hiroyuki Taniguchi 1-32 Chayacho, Kita-ku, Osaka-shi, Osaka Yanmar Diesel Co., Ltd.

Claims (7)

[Claims] 1. An electro-hydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve, a mechanically controlled mechanical spool valve is provided, and the increase or decrease of the fuel injection amount is controlled by the electronic spool valve. An electro-hydraulic governor provided with a switching valve for selectively switching between control and control by a mechanical spool valve. 2. An electronic hydraulic governor for increasing / decreasing a fuel injection amount using an electronically controlled electronic spool valve, comprising: an electronic spool valve and an actuator for controlling the operation of the electronic spool valve. An electro-hydraulic governor, wherein an operation direction of a valve and an actuator is arranged so as to be horizontal and perpendicular to a traveling direction of an object on which the electro-hydraulic governor is mounted. 3. An electro-hydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve, wherein a mechanically controlled mechanical spool valve is provided, and the increase or decrease of the fuel injection amount is controlled by the electronic spool valve. An electro-hydraulic governor comprising a switching valve for selectively switching between control and control by a mechanical spool valve, wherein the switching valve is formed in the electronic spool valve. 4. An electro-hydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve, a mechanically controlled mechanical spool valve is provided, and the increase or decrease of the fuel injection amount is controlled by the electronic spool valve. An electro-hydraulic characterized by comprising a switching valve for selectively switching between control and control by a mechanical spool valve, and a compensator mechanism acting on both the electronic spool valve and the mechanical spool valve. Governor. 5. An electrohydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve, wherein a separate case having an electronic control unit for controlling the electrohydraulic governor is mounted on the governor body. Thus, the lead wires of the electronic control unit are collectively pulled out from the upper surface of the separate case, and
An electro-hydraulic governor wherein an air breather which seals a space between the lead wire and the upper surface of the separate case with a seal member and communicates a space inside the governor main body with the outside is attached to the upper surface of the governor main body. 6. An electrohydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve, wherein a separate case having an electronic control unit for controlling the electrohydraulic governor is provided on one surface of the governor body. Attaching, attaching a temperature sensor to the opposite side of the governor main body from the separate case mounting surface,
An electrohydraulic governor wherein the temperature sensor is disposed near an electronic spool valve. 7. An electrohydraulic governor for increasing or decreasing a fuel injection amount by using an electronically controlled electronic spool valve, a mechanically controlled mechanical spool valve is provided, and the increase or decrease of the fuel injection amount is controlled by the electronic spool valve. A switching valve that selectively switches between control and control by a mechanical spool valve is provided, and when control is performed by a mechanical spool valve, the output limit range when control is performed by an electronic spool valve is not exceeded. Electro-hydraulic governor characterized by such control.