JPH08145081A - Rotary speed control device for wet type multiplate hydraulic clutch - Google Patents

Abstract

PURPOSE: To improve control accuracy of rotary speed of the output side of a wet type multiplate hydraulic clutch. CONSTITUTION: A device is formed in such a constitution that the inner disk and the outer disk of a wet type multiplate hydraulic clutch are tightly fitted by a hydraulic cylinder unit 4 which rotates integratedly with the inner disk, and rotary speed is controlled at the time of operation in a slip condition. A prime mover 1 which rotates at set rotary speed is connected to a first shaft, and the output side of the wet type multiplate hydraulic clutch 3 is connected to a second shaft through a power transmission mechanism. A differential gear device 7 is provided so as to output a rotary speed difference between the output side rotary speed of the wet type multiplate hydraulic clutch 3 and set rotary speed from a third shaft which is connected to the first and second shafts through a differential gear mechanism. And also an operating oil pressure controlling means 8 is provided so as to control pressure of operating oil which is supplied to the hydraulic cylinder unit 4 according to the output result of the differential gear device 7.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary speed control device for a wet multi-plate hydraulic clutch, and more particularly, to a generator, a refrigerating device, an air conditioner, etc. mounted on a ship, a vehicle or the like by a prime mover. The present invention relates to a rotation speed control device for a wet multi-plate hydraulic clutch used when rotating at a required rotation speed.

[0002]

2. Description of the Related Art For example, in ships, in order to reduce operating expenses and cope with an increasing tendency of electric power consumption during operation, a surplus of a main engine with high engine efficiency is used instead of a diesel generator that has been used before. 2. Description of the Related Art A marine generator drive device (commonly called “axial generator”) that uses power to drive a generator has been used.

Conventionally, as this type of marine generator drive (shaft generator), a main engine and a generator are connected via a wet multi-plate hydraulic clutch to change the operating hydraulic pressure of the wet multi-plate hydraulic clutch. A method of controlling the rotation speed of the generator by utilizing the slip characteristic due to the above is adopted. In order to transmit power at a required rotational speed using this wet multi-plate hydraulic clutch, a hydraulic system that rotates an inner disk (clutch plate) and an outer disk (clutch plate) integrally with the inner disk from the side surface is used. It is necessary to press the cylinder unit to form an oil film between the two disks and to maintain a slip state between the two disks. Therefore, the pressing force of the hydraulic cylinder unit, that is, the pressure of the hydraulic oil for operating the hydraulic cylinder unit (the operating hydraulic pressure) )
Need to be adjusted.

As a method of adjusting the operating hydraulic pressure of the hydraulic cylinder unit, a hydraulic multiple valve such as an electromagnetic proportional control valve and a pressure servo valve is used to detect a rotational speed on the output side of the wet multi-plate hydraulic clutch and to set a rotational speed. Or a method of controlling the hydraulic valve according to the rotational speed difference, or detecting each rotational speed on the input / output side of the wet type multi-plate hydraulic clutch to determine the rotational speed difference, and calculating the hydraulic pressure according to the rotational speed difference. A method of controlling a valve or the like is employed.

There is also a system in which a centrifugal valve is built in the rotating body on the output side of the wet multi-plate hydraulic clutch, and the pressure is controlled by operating the element by utilizing the centrifugal force acting on the element of this valve. In this method, it is possible to continuously detect fluctuations in the rotational speed and to continuously set the pressure of the hydraulic cylinder unit that sets the inner disk and the outer disk of the wet-type multi-plate hydraulic clutch in close contact with each other.

[0006]

However, in the case of the conventional apparatus for controlling the rotational speed by adjusting the operating oil pressure of the hydraulic cylinder unit, there are the following problems. That is, in the feedback control method using the hydraulic valve,
It is difficult to adopt a path control that controls the temporal change of the rotational speed, that is, acceleration / deceleration, and it is also difficult to adopt a pseudo path control that continuously performs similar position control. When the rotation speed of the motor changes greatly, the response to the change of the rotation speed is poor. In the control method using the centrifugal valve, since a tangential force acts on the element of the centrifugal valve other than the centrifugal force, it is affected by this tangential force, and when the rotation speed fluctuates, The centrifugal valve element will be affected by acceleration / deceleration besides rotation speed,
In particular, when the acceleration / deceleration is large (when the change in the rotation speed for a short time is large), the pressure set in the hydraulic cylinder unit is different from the actual pressure. As described above, the conventional rotation speed control device has poor response to short-term load fluctuations and rotation speed fluctuations.
There is a problem such as.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and has as its object to provide a wet-type multi-plate hydraulic clutch in which the output-side rotational speed control accuracy of the wet-type multi-plate hydraulic clutch is improved. Another object of the present invention is to provide a rotation speed control device.

[0008]

The rotational speed control device for a wet multi-plate hydraulic clutch according to claim 1 of the present invention as means for achieving the above object rotates on a first shaft at a set rotational speed. A third unit connected to a prime mover, connected to a second shaft via a power transmission mechanism to an output side of a wet multi-plate hydraulic clutch, and connected to the first and second shafts via a differential gear mechanism.
A differential gear device that outputs a rotational speed difference between an output rotational speed of the wet multi-plate hydraulic clutch and a set rotational speed from a shaft, and an operation of supplying the differential to the hydraulic cylinder unit according to a detection result of the differential gear device An operating pressure control means for controlling the oil pressure is provided.

According to a second aspect of the present invention, there is provided a wet multi-plate hydraulic clutch rotational speed control apparatus according to the first aspect, wherein the operating pressure control means includes the differential gear. Rotation / linear conversion means for converting the output of the third axis of the device into linear motion; pressure conversion means for converting the conversion result of the rotation / linear conversion means into pressure; And a pressure control means for controlling the pressure of the hydraulic oil supplied to the hydraulic cylinder unit. Further, according to a third aspect of the present invention, in the rotation speed control device for a wet-type multi-plate hydraulic clutch according to the second aspect, an accumulator is connected to an output side of the pressure conversion unit. It has a configuration. Further, the rotational speed control device for a wet-type multi-plate hydraulic clutch according to claim 4 of the present invention is the above-mentioned claim 2.
In the rotational speed control device of the wet multi-plate hydraulic clutch of
A buffer member is interposed between the rotation / linear conversion means and the pressure conversion means.

According to a fifth aspect of the present invention, there is provided a wet multi-plate hydraulic clutch rotational speed control device according to the first aspect, wherein the wet multi-plate hydraulic clutch rotational speed control device has an operating pressure control means of the differential gear device. An electric signal converting means for converting an output into an electric signal, an electromagnetic pressure control valve for controlling the pressure of the working hydraulic pressure supplied to the hydraulic cylinder unit, and the electromagnetic pressure control valve according to the conversion result of the electric signal converting means. The control valve control means for controlling is provided. According to a sixth aspect of the present invention, there is provided a wet multi-plate hydraulic clutch rotation speed control device according to the fifth aspect, in which the electric signal conversion means detects the differential gear device. The conversion result of the rotation / linear conversion means for converting the rotational speed difference into linear motion is converted into an electric signal.

According to a seventh aspect of the present invention, there is provided a rotational speed control device for a wet multi-plate hydraulic clutch, wherein a hydraulic pump is connected to an input side of the wet multi-plate hydraulic clutch and a hydraulic pump / motor is connected to an output side thereof. The discharge side of the hydraulic pump and the suction side of the hydraulic pump / motor are connected via a flow control valve.

[0012]

The rotary speed control device for a wet multi-plate hydraulic clutch according to the first aspect of the present invention is connected to the output side of the wet multi-plate hydraulic clutch via the prime mover rotating at the set rotary speed and the power transmission mechanism. The rotation speed difference between the output rotation speed and the set rotation speed of the wet multi-plate hydraulic clutch is output from the third shaft connected to the first shaft and the second shaft via the differential gear mechanism, and the rotation speed difference is determined according to this rotation speed difference. By controlling the pressure of the hydraulic oil supplied to the hydraulic cylinder unit by the operating pressure control means, the difference between the output side rotation speed and the set rotation speed of the wet multi-plate hydraulic clutch is continuously detected, and the detection result Is converted into the operating hydraulic pressure of the hydraulic cylinder unit, and acts so as to maintain the output side rotation speed of the wet multi-plate hydraulic clutch at the set rotation speed with high accuracy.

According to a second aspect of the present invention, there is provided a rotational speed control apparatus for a wet-type multi-plate hydraulic clutch which converts a rotational speed difference detected by a differential gear device into linear motion by a rotational / linear converting means. After converting the result to pressure by pressure conversion means,
By operating the pressure control means with this pressure to control the pressure of the working oil supplied to the hydraulic cylinder unit, the working pressure can be set in a short time even when the rotational speed difference is large. By connecting an accumulator to the output side of the pressure conversion means, or by interposing a buffer member between the rotation / linear conversion means and the pressure conversion means, it acts to prevent sudden pressure fluctuations of the hydraulic cylinder unit. .

The rotating speed control device for a wet multi-plate hydraulic clutch according to claims 5 to 6 of the present invention converts the rotating speed difference detected by the differential gear device into an electric signal by the electric signal converting means, and the conversion result is obtained. Accordingly, the control valve control means controls the electromagnetic pressure control valve that controls the pressure of the hydraulic oil supplied to the hydraulic cylinder unit, thereby operating the operation pressure control means in a simplified manner. The same effect is obtained by converting the conversion result of the rotation / linear converter, which converts the rotational speed difference detected by the differential gear device into linear motion, into an electrical signal.

According to a seventh aspect of the present invention, there is provided a rotational speed control apparatus for a wet-type multi-plate hydraulic clutch, wherein a hydraulic pump is connected to an input side of a wet-type multi-plate hydraulic clutch, and a hydraulic pump / motor is connected to an output side. Since the discharge side of the pump and the suction side of the hydraulic pump / motor are connected via a flow control valve, and the flow control valve is connected to the discharge side of the hydraulic pump / motor, the output of the wet multi-plate hydraulic clutch is When the side rotation speed fluctuates suddenly, the fluctuation is suppressed, and the rapid rotation speed fluctuation is changed to a slow rotation speed fluctuation, so that the control system that controls the operating oil pressure according to the rotation speed difference acts to respond. .

[0016]

Embodiments of the present invention will be described below with reference to the drawings. Here, FIG. 1 to FIG.
1 shows an embodiment of the present invention, FIG. 1 is an overall block diagram of the first embodiment, FIG. 2 is a detailed configuration diagram of an operating hydraulic control system of FIG. 1, and FIG. 3 is a hydraulic pump and a hydraulic pump motor system of FIG. FIG. 4 is a detailed circuit diagram, FIG. 4 is a sectional view of an essential part of the differential gear device of FIG. 2, FIG. 5 is a hydraulic circuit diagram of an essential part showing a second embodiment, and FIG. .

The wet-type multi-plate hydraulic clutch rotational speed control apparatus according to the present embodiment is a rotational-speed control apparatus used when a generator is driven by the output of a main engine of a ship via a wet-type multi-plate hydraulic clutch. In brief, a wet multi-plate hydraulic clutch 3 is provided between a prime mover 1 as a main engine and a generator 2 as a follower.
Is provided, and hydraulic oil is supplied from a hydraulic oil supply unit 5 to a hydraulic cylinder unit 4 of the wet multi-plate hydraulic clutch 3,
A differential for transmitting the rotation with the wet multi-plate hydraulic clutch 3 connected and connecting the motor 6 rotating at a set rotation speed and the output side of the wet multi-plate hydraulic clutch 3 to detect and output a difference in the rotation speed. The gear device 7 and the differential gear device 7
And an operating oil pressure control unit 8 for controlling the pressure of the operating oil supplied to the hydraulic cylinder unit 4 in accordance with the output of the hydraulic multi-plate hydraulic clutch 3 to continuously determine the difference between the output rotation speed of the wet multi-plate hydraulic clutch 3 and the set rotation speed. By detecting and controlling the operating oil pressure of the hydraulic cylinder unit 4 to control the rotation speed, a hydraulic pump 9 is connected to the input side of the wet multi-plate hydraulic clutch 1 and a hydraulic pump / motor 10 is connected to the output side. The discharge side of the hydraulic pump 9 and the suction side of the hydraulic pump / motor 10 are connected via a flow control valve 11, and the hydraulic pump / motor 10
A flow control valve is connected to the discharge side to prevent a sudden change in the rotational speed, enable a response of the hydraulic control system, and stably improve the control accuracy.

The prime mover 1 is connected via a shaft coupling 21 to a shaft 23 of a drive gear 22 of a parallel-shaft single-stage gearbox, and a shaft 25 of a driven gear 24 meshing with the drive gear 22 is connected to the wet multi-plate hydraulic clutch 3. Connect the input side, wet multi-plate hydraulic clutch 3
Is connected to an output shaft 26, and the marine generator 2 is connected to the output shaft 26 via a shaft coupling 27. The wet multi-plate hydraulic clutch 3 includes an inner disk 3a and an outer disk 3
b is pressed by the piston member 4a of the hydraulic cylinder unit 4 rotating integrally with the inner disc 3a to form an oil film between both discs 3a and 3b and maintain a slip state between both discs 3a and 3b. The rotation on the input side is transmitted to the output side.

As shown in FIG. 2, the hydraulic oil supply unit 5 sucks hydraulic oil from an oil tank unit 34 by a hydraulic pump 33 which is rotationally driven by a motor 31 through a shaft coupling 32, and drives the driven gear through a pipe 35. The hydraulic oil supply device 36 provided on the shaft 25 of the 24 is configured to supply hydraulic oil to the hydraulic cylinder unit 4 through an oil passage formed in the shaft 25, and a pressure control valve 37 is provided by branching from the pipe 35. ing.

The differential gear device 7 includes four operating gears 41 to 41 which constitute a differential gear mechanism 40 as shown in FIGS.
A shaft coupling 4 is attached to a first shaft 45 connected to a gear 41 of the shafts 44.
6, the variable-speed prime mover 6 rotating at a set rotation speed is connected, and the output side of the wet multi-disc hydraulic clutch 3 is connected to a second shaft 47 connected to the gear 42 via a shaft coupling 48,
A gear 49 is connected to the gears 43 and 44 that rotate according to the rotational speed difference between the shaft 45 and the second shaft 47, the gear 50 is meshed with this gear 49, and the gear 50 is provided with the third shaft 51. .

The differential gear device 7 includes a first shaft 45 and a second shaft 45.
The rotation direction of the shaft 47 is set to be the same as viewed from the shaft end. When the rotation speeds of the first shaft 45 and the second shaft 47 are the same, the gear 49 does not rotate, and the first shaft 45 does not rotate. When a rotational speed difference is generated between the motor and the second shaft 47, the high rotational speed shaft becomes the drive shaft, the low rotational speed shaft becomes the driven shaft, and the gear 49 rotates at half the rotational speed difference. To rotate in either the forward or reverse direction, and this rotation is reduced by the gear 50 to rotate the third shaft 51. Therefore, the rotation speed of the third shaft 51 is set to the set rotation speed and the wet multi-plate hydraulic clutch 3 The rotation speed is different from the rotation speed on the output side, or the rotation speed is proportional to the rotation speed difference.

As shown in FIG. 2, the operating hydraulic pressure control unit 8 includes a rotation / linear conversion mechanism 53 for converting the rotation of the third shaft 51 of the differential gear device 7 into a linear motion, and a rotation / linear conversion mechanism 5
3. A hydraulic cylinder unit 54 for converting the linear motion converted into the pressure into a pressure, and a pressure control valve for controlling the pressure of the hydraulic oil supplied from the hydraulic oil supply unit 5 in accordance with the pressure generated by the hydraulic cylinder unit 54 55. Here, the rotation / linear conversion mechanism 53 is composed of a nut connected to the third shaft 51 via a clutch 74 and a screw rod meshing with the nut, and the end of the screw rod is connected to the cylinder 54 a of the hydraulic cylinder unit 54. A piston rod 54b that slides inside is connected, and an oil chamber in the cylinder 54a is communicated with a pilot oil chamber 55a of the pressure control valve 55.
By controlling the opening and closing of c, the pressure of the hydraulic oil supplied to the hydraulic cylinder unit 4 is controlled.

Further, an accumulator 57 is connected to the operating hydraulic control unit 8 between the cylinder 54a of the hydraulic cylinder unit 54 and the pilot oil chamber 55a of the pressure control valve 55 via a stop valve 56, and the pressure control valve 58 is Connected. The accumulator 57 suppresses a sudden pressure change of the hydraulic cylinder unit 54. The parts of the prime mover 6, the differential gear unit 7 and the hydraulic pressure control unit 8 excluding the pressure control valve 55 are remote control devices 59.
It is constituted as.

On the other hand, the hydraulic pump 9 is connected to the shaft 25 of the driven gear 24 to which the input side of the wet multi-plate hydraulic clutch 3 is connected via the shaft coupling 60, and the gear 61 provided on the output shaft 26.
The hydraulic pump / motor 10 is connected to the shaft 63 of the gear 62 meshing with the hydraulic pump / motor 10 via a shaft coupling 64, and the discharge side of the hydraulic pump 9 and the suction side of the hydraulic pump / motor 10 are connected via a pipe 65, The flow control valve 11 is interposed in the pipe 65, and an electromagnetic direction switching valve 66 is provided between the flow control valve 11 and the hydraulic pump 9.

The discharge side of the hydraulic pump 9 is connected to the tank 34 via a pressure assurance valve 67, and the flow control valve 11 of the pipe 65 and the hydraulic pump / motor 10 are connected to the tank via a check valve 68. 34, a flow control valve 69 with pressure / temperature compensation is connected to the discharge side of the hydraulic pump / motor 10, and also connected to the tank 34 via a pressure control valve 70.

The operation of the rotation speed control apparatus for a wet-type multi-plate hydraulic clutch according to this embodiment will be described.
, The parallel shaft type gearbox starts operating, the input side of the wet-type multi-plate hydraulic clutch 3 rotates via the drive gear 22 and the driven gear 24, and the driven gear 24
The hydraulic pump 9 connected to the shaft 25 is operated to discharge the hydraulic oil, but the hydraulic oil is returned to the tank 34 via the pressure assurance valve 67 because the electromagnetic direction switching valve 66 is not excited.

Next, the electromagnetic directional control valve 66 is excited to supply the hydraulic oil discharged from the hydraulic pump 9 to the hydraulic pump / motor 10. The supply flow rate at this time is the flow rate set by the flow rate control valve 11, and the set flow rate is a flow rate corresponding to the rotation speed set on the output side of the wet multi-plate hydraulic clutch 3. With respect to the hydraulic pump / motor 10, the pressure loss caused by the flow control valve 69 with pressure / temperature assurance and the piping 65 acts as a back pressure, but operates as a hydraulic motor, and the wet multi-plate hydraulic clutch 3 is operated.
Operate at the rotation speed set on the output side of. When the output rotation speed of the wet multi-plate hydraulic clutch 3 is stabilized at the set rotation speed, the electric motor 31 of the hydraulic oil supply unit 5 is started, and after a certain period of time, the electromagnetic valve 37 a attached to the pressure control valve 37 is excited. . The hydraulic pump 33 discharges hydraulic oil at an initial pressure set for the pressure control valve 55, and the hydraulic oil is supplied to the hydraulic cylinder unit 4 of the wet multi-plate hydraulic clutch 3. Is in the “fit” state.
Here, the initial pressure set in the pressure control valve 55 is performed by the spring 55b, and the initial pressure is to make the state between the inner disk 3a and the outer disk 3b of the wet multi-plate hydraulic clutch 3 as stable as possible, that is, to make the wet state. Therefore, the pressure is set so that both disks 3a and 3b are lightly adhered to each other.

At this point, the wet-type multi-plate hydraulic clutch 3 operates as a hydraulic brake for the hydraulic pump / motor 10 because the hydraulic pump / motor 10 operates as a hydraulic motor. That is, the hydraulic pump / motor 10
The output torque of the hydraulic multi-plate hydraulic clutch 3 is gradually increased by the operation of the hydraulic oil supply unit 5.
When the initial pressure is applied to the hydraulic cylinder unit 4, the torque acts as a brake.

On the other hand, at the same time as exciting the electromagnetic valve 37a attached to the pressure control valve 37 of the hydraulic oil supply section 5, the variable speed electric motor 6 of the remote control device 59 is started. At this time, the third shaft 51 of the differential gear unit 7 rotates, but the clutch 74 is in the “disengaged” state, so that the rotation / linear conversion mechanism 53 does not operate. The third shaft 51 of the differential gear device 7 rotates in the forward or reverse direction when there is a difference between the set rotation speed and the output-side rotation speed of the wet multi-plate hydraulic clutch 3. Differential gearing 7
When the clutch 74 is set to the engaged state at the time when the rotation speed of the third shaft 51 reaches the allowable rotation speed, the rotation of the third shaft 51 is converted into linear motion (forward / backward motion) by the rotation / linear conversion mechanism 53. When the piston rod 54b of the hydraulic cylinder unit 54 moves in or out of the cylinder 54a, the pressure in the cylinder 54a changes, thereby changing the pilot pressure of the pressure control valve 55. The operating pressure supplied to the hydraulic cylinder unit 4 of the multiple disc hydraulic clutch 3 changes.

For example, when the output rotation speed of the wet-type multi-plate hydraulic clutch 3 is lower than the set rotation speed, the third shaft 51 of the differential gear unit 7 rotates in the forward direction, via the rotation / linear conversion mechanism 53. When the piston rod 54b of the hydraulic cylinder unit 54 enters the cylinder 54a, the pressure in the cylinder 54a increases, whereby the pilot pressure of the pressure control valve 55 increases, and the wet multi-plate hydraulic clutch 3 The hydraulic pressure supplied to the hydraulic cylinder unit 4 is increased, so that the slip of the wet-type multi-plate hydraulic clutch 3 decreases and the output-side rotation speed increases.

Conversely, when the output rotation speed of the wet multi-plate hydraulic clutch 3 is higher than the set rotation speed, the differential gear device 7
The third shaft 51 rotates in the opposite direction, and the piston rod 54b of the hydraulic cylinder unit 54 retreats with respect to the cylinder 54a via the rotation / linear conversion mechanism 53, so that the pressure in the cylinder 54a decreases. As a result, the pilot pressure of the pressure control valve 55 decreases, and the hydraulic pressure supplied from the hydraulic pump 33 to the hydraulic cylinder unit 4 of the wet-type multi-plate hydraulic clutch 3 is reduced, so that the slip of the wet-type multi-plate hydraulic clutch 3 increases. As a result, the output side rotation speed decreases.

As described above, the control to make the hydraulic cylinder unit 4, the differential gear unit 7, the hydraulic cylinder unit 54, and the pressure control valve 55 of the wet multi-plate hydraulic clutch 3 a closed loop, that is, the feedback control is performed, and the wet multi-plate hydraulic The output rotation speed of the clutch 3 acts so as to be set and maintained at the set rotation speed.

When the clutch 74 is engaged, a load is applied to the generator 2 driven by the wet multi-plate hydraulic clutch 3. When the load of the generator 2 becomes equal to or greater than a preset value, the flow rate supplied to the hydraulic pump / motor 10 is reduced by operating the flow control valve 11, and the operating state is temporarily changed from the hydraulic motor to the hydraulic pump. Conversion. The supply flow rate from the hydraulic pump 9 thereafter becomes the flow rate set by the flow control valve 11. When the required flow rate of the hydraulic pump / motor 10 is smaller than this flow rate, the hydraulic pump / motor 10 operates as a hydraulic motor, In many cases, the hydraulic pump / motor 10 operates as a hydraulic pump. The insufficient flow rate of the hydraulic pump / motor 10 is self-priming through the check valve 68. By exciting the electromagnetic directional control valve 66 in this way, the input side and the output side of the wet multi-plate hydraulic clutch 3 are hydraulically connected.

Therefore, when a load is applied to the generator 2, the load on the wet multi-plate hydraulic clutch 3 is increased at this point, but the inner disk 3a and the outer disk 3b are increased.
Cannot be instantaneously changed, and as a result, the slip between the disks 3a and 3b increases and the rotation speed decreases. Thereby, the hydraulic pump / motor 10
Of the hydraulic pump / motor 10
Is converted into a hydraulic motor and acts to increase the rotational speed of the wet multi-plate hydraulic clutch 3 on the output side. Along with that
Since the third shaft 51 of the differential gear device 7 rotates and the pressure control valve 55 acts to increase the working hydraulic pressure for the hydraulic cylinder unit 4 as described above, the wet multi-plate hydraulic clutch 3 reduces slip. The output side rotation speed increases. This effect is the same not only when the load is applied but also when the load is increased during the normal operation.

If the load is instantaneously cut off while the generator 2 is operating under load, slippage is reduced because the contact state between the disks 3a and 3b of the wet multi-plate hydraulic clutch 3 is in the state before the load is cut off. Thus, the output side rotation speed of the wet multi-plate hydraulic clutch 3 increases and the hydraulic pump / motor 10 also increases in speed, whereby the hydraulic pump / motor 10 operates as a hydraulic pump, and the set flow rate of the flow control valve 69 is changed. Since the excess flow rate flows out at the set pressure of the pressure control valve 70, braking is applied to the output side of the wet multi-plate hydraulic clutch 3 and the rotation speed is reduced. At the same time, the differential gear device 7
The third shaft 51 rotates in the reverse direction, and the pressure control valve 55 acts to reduce the operating oil pressure to the hydraulic cylinder unit 4 as described above. It operates and the output side rotation speed decreases. This effect is the same not only when the load is interrupted but also when the load is reduced during normal operation.

If the load fluctuation is small and the fluctuation range of the rotation speed is within the setting range of the flow control valve 11 and the flow control valve 69 with pressure / temperature compensation, the hydraulic pump / motor 10
Becomes no-load operation.

As described above, the rotation speed control device for a wet-type multi-plate hydraulic clutch according to the present embodiment does not control a temporal change in the rotation speed, but performs a feedback control for a mere change in the rotation speed. Therefore, the position control is performed instead of the path control. However, by inputting the output rotation speed and the set rotation speed of the wet multi-plate hydraulic clutch 3 to the differential gear mechanism 40 incorporated in the differential gear device 7, The rotational speed difference can be continuously detected as a half of the rotational speed by the characteristics of the gear mechanism 40, and the pressure control valve 55 is controlled in accordance with the detected rotational speed difference to control the wet multi-plate hydraulic clutch 3 The hydraulic pressure supplied to the hydraulic cylinder unit 4 can be continuously controlled, so that pseudo-path control similar to path control can be performed, and the hydraulic pump 9, the hydraulic pump / motor 10, etc. It is not also act as the response becomes faster with respect to the rotational speed variation of the output side due to rotation speed fluctuation occurring on the input side with the exception of the instantaneous rotation speed fluctuation due to load fluctuation.

Here, by detecting the difference between the output rotation speed of the wet-type multi-plate hydraulic clutch 3 and the set rotation speed by using the characteristics of the differential gear mechanism, it is possible to detect with extremely high sensitivity. . That is, the control target of the frequency of generated electricity is ± 0.5 Hz.
It is ± 10 min-1 because of the operation at, but it is possible to detect the rotation speed up to this value or less. When the detected value is directly used for the pressure control valve 55, the sensitivity becomes extremely high, and therefore the sensitivity is slightly lowered by the accumulator 57. Here, this sensitivity adjustment can be performed based on the volume of the hydraulic cylinder unit 54, the amount of gas charged in the accumulator 57, and the pressure, and the sensitivity increases as the gas charged capacity of the accumulator 57 decreases.

By the way, even if the pseudo-path control is used as described above, due to the structure of the wet-type multi-plate hydraulic clutch, the instantaneous load fluctuation,
It is difficult to deal with fluctuations in rotation speed. That is,
Power transmission in a wet multi-plate hydraulic clutch depends on the thickness of the oil film between the inner disk and the outer disk, the pressure of the oil film, and the characteristics of the hydraulic oil. It is clear that slipping between the two disks is the most unstable state, and the state between the two disks is instantaneously or instantaneously changed in response to a sudden or instantaneous change in the transmission torque. It is difficult to follow a temporal change, and as a result, the output side rotational speed fluctuates, and this tendency is remarkable in a load increase under a light load or a load decrease in a heavy load (especially load interruption). Becomes

Therefore, a hydraulic pump 9, a hydraulic pump / motor 10 and a flow rate control valve 11 are provided in parallel with the wet multi-plate hydraulic clutch 3 so that the hydraulic pump / motor 10 can be used as a hydraulic motor against a decrease in rotation speed due to an increase in load. Since the rotation speed is increased by operating it and the rotation speed is decreased by operating the hydraulic pump / motor 10 as a hydraulic pump in response to the increase in rotation speed due to the decrease in load.
Sudden changes in the output-side rotation speed of the wet-type multi-plate hydraulic clutch are suppressed, resulting in a slow change in the rotation speed, and it is possible to sufficiently cope with the pseudo-path control. This effect is
Significant changes can be obtained against sudden changes in load such as load input during light load operation and load rejection during load operation.
When it is within the setting range of 9, the hydraulic pump / motor 10 is in a no-load operation and does not act as a load on the wet-type multi-plate hydraulic clutch 3 and does not affect the operation hydraulic control. In addition,
By using a piston type with high volumetric efficiency as the hydraulic pump / motor 10, a remarkable effect against a sudden change in rotation speed can be obtained.

Here, whether the hydraulic pump / motor 10 is used as a hydraulic pump or as a hydraulic motor is determined by the flow rate setting for the flow control valves 11 and 69, but there is a certain flow rate difference between them. Flow control valve 1
The set flow rate of the flow control valve 69 must be increased with respect to 1. Further, the set flow rate for the flow rate control valves 11, 69 is set to a flow rate slightly deviating from the set rotational speed for the wet multi-plate hydraulic clutch 3. The ratio of the power transmission capacity of the combination of the hydraulic pump 9 and the hydraulic pump / motor 10 to the power transmission capacity of the wet multi-plate hydraulic clutch 3 is set to 1: 0.15 in the embodiment. In addition, hydraulic pump
Although the braking force when the motor 10 is used as a hydraulic pump varies depending on the rotation speed, the maximum braking force is set to about 40% of the power transmission capacity of the wet multi-plate hydraulic clutch 3. Even with such a setting, a sufficient effect can be exhibited.

In place of the accumulator 57 in the above embodiment, the hydraulic cylinder unit 54 and the rotation / linear conversion mechanism 53 are connected via a spring or other buffer member, and the rotational speed difference detected by the differential gear device 7 is connected. It is also possible to prevent an abrupt pressure change when converting to pressure. However, in this case, when the pilot pressure of the pressure control valve 55 changes, a difference occurs between the compression ratio of the scum and the spring constant of the spring. That is, when the rotational speed difference is large, the pilot pressure tends to increase, albeit slightly, but there is no problem in practical use.

Next, the second embodiment shown in FIG.
This is an example in which the pressure control valve 55 in the embodiment is interposed in the pipe 35 passing through the hydraulic pump 33 and the hydraulic cylinder unit 4, and other configurations are the same as those in the first embodiment. Even in this case, the same operation and effect as in the first embodiment can be obtained.

Further, the third embodiment shown in FIG.
The pressure control valve 55 of the embodiment is changed to an electromagnetic proportional relief valve 71 which is an electromagnetic control valve capable of electrically controlling remotely, and a rotation / linear conversion for converting the rotation of the third shaft 51 of the differential gear device 7 into a linear motion. A setter 72, which is an electric signal converting means for converting the linear movement of the mechanism 53 into an electric signal, and a controller 73, which is a control valve control means for controlling the electromagnetic proportional relief valve 71 in accordance with the electric signal of the setter 72, are provided. It is a thing.

In this case, the same operation and effect as in the above embodiment can be obtained. In this case, due to the mechanical and fluid operation delay of the electromagnetic proportional relief valve 71 with respect to the electric signal, the setting of the operating hydraulic pressure of the hydraulic cylinder unit 4 by the electromagnetic proportional relief valve 71 is small when the rotational speed difference is large. Although it tends to be delayed, this is not a problem in practical use. Further, instead of the electromagnetic proportional relief valve 71, an electromagnetic proportional pressure reducing valve, a pressure servo valve, or the like can be used. Further, the rotation of the third shaft 51 of the differential gear device 7 can be directly converted into an electric signal.

It should be noted that the present invention is not limited to the above-described embodiment, but includes a configuration that can be modified and implemented without changing the gist of the present invention. By the way, in the above embodiment, an example in which the present invention is applied to a drive device of a marine generator has been described. However, for example, the present invention may be applied to a drive device of a generator of a vehicle, an air conditioner, or a drive device of a refrigeration / refrigeration device. Can be.

[0047]

As is apparent from the above description, according to the rotation speed control apparatus for a wet-type multi-plate hydraulic clutch according to the first aspect of the present invention, the wet-type multi-plate hydraulic clutch has a wet-type motor via a prime mover rotating at a set rotation speed and a power transmission mechanism. The output rotation speed and the set rotation speed of the wet multi-disc hydraulic clutch from a first shaft and a second shaft respectively connected to the output side of the multi-disc hydraulic clutch and a third shaft connected via a differential gear mechanism. Since the difference in rotation speed is output and the pressure of the working oil supplied to the hydraulic cylinder unit is controlled by the working pressure control means according to the difference in rotation speed, the output rotation speed and the set rotation speed of the wet multi-plate hydraulic clutch are controlled. The difference from the speed can be continuously detected to control the hydraulic pressure of the hydraulic cylinder unit continuously, and the output rotation speed of the wet multi-plate hydraulic clutch can be maintained at the set rotation speed with high accuracy. When With a cormorant effect.

According to the rotational speed control device for a wet-type multi-plate hydraulic clutch according to the second aspect of the present invention, the rotational speed difference detected by the differential gear device is converted into linear motion by the rotation / linear conversion means, and this conversion is performed. The result is converted into pressure by the pressure conversion means, and the pressure control means is operated with this pressure to control the pressure of the hydraulic oil supplied to the hydraulic cylinder unit. There is an effect that setting can be performed in a short time.

According to the rotational speed control device for a wet multi-plate hydraulic clutch of claims 3 to 4 of the present invention, in addition to the effect of claim 2, an accumulator is connected to the output side of the pressure converting means, or rotation / rotation / rotation / rotation / rotation / rotation / rotation / rotation / rotation / rotation Since the cushioning member is interposed between the straight line conversion means and the pressure conversion means, it is possible to prevent an abrupt pressure change in the hydraulic cylinder unit.

According to the rotation control apparatus for a wet-type multi-plate hydraulic clutch according to claims 5 to 6 of the present invention, the rotational speed difference detected by the differential gear device by the electric signal conversion means is used as it is, or the rotational speed difference is linearly moved. The electromagnetic pressure control unit controls the pressure of the hydraulic oil supplied to the hydraulic cylinder unit by the control valve control unit according to the conversion result. Is simplified.

According to the rotational speed control apparatus for a wet-type multi-plate hydraulic clutch of the present invention, a hydraulic pump is connected to the input side of the wet-type multi-plate hydraulic clutch, and a hydraulic pump / motor is connected to the output side. Since the discharge side of these hydraulic pumps and the suction side of the hydraulic pump / motor are connected via a flow control valve, it is possible to suppress the fluctuation when the output rotation speed of the wet multi-plate hydraulic clutch fluctuates rapidly. In addition to this, rapid rotation speed fluctuations can be changed to slow rotation speed fluctuations in accordance with this, and there is an effect that a control system for controlling the operating oil pressure can respond according to the rotation speed difference. Further, at the time of starting, since the load is light, the setting of the rotation speed by the wet-type multi-plate hydraulic clutch is very unstable due to its structure. At this point, the hydraulic pump
By operating the motor as a hydraulic motor, it is possible to set the rotation speed on the output side of the wet multi-plate hydraulic clutch to the set rotation speed, so that the unstable state at the time of starting the wet multi-plate hydraulic clutch can be corrected. It has the effect of being able to.

As described above, according to the rotation speed control apparatus for a wet type multi-plate hydraulic clutch of the present invention, it is possible to provide a device capable of stably controlling the output side rotation speed of the wet type multi-plate hydraulic clutch with high accuracy. It has the effect of.

[Brief description of drawings]

FIG. 1 is an overall block diagram of a first embodiment of the present invention.

FIG. 2 is a detailed configuration diagram of a hydraulic control system of FIG. 1;

FIG. 3 is a detailed circuit diagram of a hydraulic pump and a hydraulic pump motor system of FIG. 1;

FIG. 4 is a sectional view of a main part of the differential gear device of FIG. 2;

FIG. 5 is a main part hydraulic circuit diagram showing a second embodiment of the present invention.

FIG. 6 is a main part configuration diagram showing a third embodiment of the present invention.

[Explanation of symbols]

1 ... prime mover (main engine), 2 ... generator, 3 ...
Wet multi-plate hydraulic clutch, 4 ... hydraulic cylinder unit, 5 ... hydraulic oil supply unit, 6 ... motor, 7 ...
Differential gear device, 8 ... hydraulic pressure control unit, 9 ... hydraulic pump, 10 ... hydraulic pump / motor, 11 ... flow control valve, 40 ... differential gear mechanism, 45 ...・ First
Axis, 48 ... Second axis, 51 ... Third axis, 53 ...
Rotation / linear conversion mechanism, 54: hydraulic cylinder unit (pressure conversion means), 55: pressure control valve (pressure control means), 68: check valve, 69: pressure / flow rate control valve, 71 ... Electromagnetic proportional relief valve (electromagnetic pressure control valve), 72 ... Setter (electric signal conversion means), 73
... Controllers (control valve control means)

Claims (7)

[Claims] 1. A wet multi-plate hydraulic clutch, wherein an inner disc and an outer disc of the wet multi-plate hydraulic clutch are brought into close contact with each other by a hydraulic cylinder unit that rotates integrally with the inner disc, and a rotational speed when operating in a slip state is controlled. In the rotational speed control device, the first shaft is connected to a prime mover that rotates at a set rotational speed, and the second shaft is connected to the output side of the wet multi-plate hydraulic clutch via a power transmission mechanism. A differential gear device that outputs a rotation speed difference between an output-side rotation speed of the wet multi-plate hydraulic clutch and a set rotation speed from a third shaft connected to two shafts via a differential gear mechanism, and the differential gear device. And a hydraulic pressure control means for controlling the pressure of the hydraulic oil supplied to the hydraulic cylinder unit according to the output result of the above. 2. The operating pressure control means converts the output of the third shaft of the differential gear device into a linear motion by a linear / linear conversion means, and converts the conversion result of the rotary / linear conversion means into a pressure. 2. The rotational speed control of a wet-type multi-plate hydraulic clutch according to claim 1, comprising: pressure conversion means; and pressure control means for controlling the pressure of hydraulic oil supplied to the hydraulic cylinder unit in accordance with a conversion result of the pressure conversion means. apparatus. 3. The wet-type multi-plate hydraulic clutch rotational speed control device according to claim 2, wherein an accumulator is connected to an output side of said pressure conversion means. 4. A rotary speed control device for a wet multi-plate hydraulic clutch according to claim 2, wherein a buffer member is interposed between the rotation / linear conversion means and the pressure conversion means. 5. An operating pressure control means, comprising: an electric signal converting means for converting an output of the differential gear device into an electric signal; an electromagnetic control valve for controlling a pressure of operating hydraulic pressure supplied to the hydraulic cylinder unit; 2. The wet-type multi-plate hydraulic clutch rotational speed control device according to claim 1, further comprising control valve control means for controlling the electromagnetic control valve in accordance with a conversion result of the electric signal conversion means. 6. The wet multi-plate according to claim 5, wherein the conversion result of the rotation / linear conversion means for converting the rotational speed difference detected by the differential gear device into linear motion is converted into an electric signal by the electric signal conversion means. Rotary speed control device for hydraulic clutch. 7. A wet-type multi-disc hydraulic clutch rotational speed control device for controlling the rotational speed when the inner disk and the outer disk of a wet-type multi-plate hydraulic clutch are brought into close contact with each other by a hydraulic cylinder unit and operating in a slip state. A hydraulic pump is connected to the input side of the wet-type multi-plate hydraulic clutch, and a hydraulic pump / motor is connected to the output side. The discharge side of the hydraulic pump and the suction side of the hydraulic pump / motor are connected via a flow control valve. A rotational speed control device for a wet type multi-plate hydraulic clutch, wherein a flow control valve is connected to a discharge side of a hydraulic pump and a motor.