JP2001058523A - Auxiliary driving device of diesel vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an auxiliary machine device of a diesel vehicle made compact and simple, and has high power transmission efficiency. SOLUTION: The auxiliary driving device of a diesel vehicle consists of an input shaft 1 which is connected with a diesel engine that changes rotation, an oilpressure multi-plate high gear clutch 2 and one way clutch 3 at the input shaft, a highspeed slide clutch 5 or a lowspeed slide clutch 15 connected through toothed gears 4, 6 with the output side of one way clutch, the highspeed stage slide clutch or the low speed stage slide clutch connected through toothed gears 7, 9 with the output side of one way clutch, auxiliary machines 11, 47 connected by the output side of each skid clutch and, actuating means of each clutch are compounded. According to the movement of the input from the input shaft 1, each slide clutch is latched and removed, and transfer efficiency of power is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an auxiliary device of a diesel vehicle, for example, a driving device such as a generator for an electric light, a compressor or a blower of a cooling device, and more particularly, to a diesel engine whose rotation speed frequently changes during running. And an auxiliary drive device for a diesel vehicle driven by the vehicle.

[0002] Generally, a diesel vehicle running with the output from a diesel engine includes a compressor for a cooling device,
A generator that generates electric power used for vehicle lighting, heating, etc.
Auxiliary equipment such as a cooling device blower for cooling the cooling water of the diesel engine and the hydraulic oil of the liquid transmission is provided.

[0003]

2. Description of the Related Art In recent years, even in diesel vehicles, the power generation capacity of a generator has been increased with an increase in the amount of electric power used, and the number of cases using an AC generator has been increasing. However, in the case of diesel vehicles, the rotational speed of the engine varies over a wide range depending on the running pattern and operating conditions of the vehicle. Required a large inverter and increased the weight of the vehicle.

Therefore, in order to eliminate such difficulties, the auxiliary equipment is driven by a hydrostatic drive device comprising a hydraulic pump driven by a diesel engine and a hydraulic motor driven by the hydraulic pump, and the operation of the auxiliary equipment is performed. An auxiliary device driving device for automatically performing control has already been proposed (Japanese Patent Laid-Open No. 10-331).
No. 680). Thus, even if the rotational speed of the diesel engine changes, the rotational speed of the generator is maintained substantially constant, and the predetermined power generation capacity of the charging generator can be maintained.

[0005] However, the above-described accessory drive device using a hydrostatic device has the following disadvantages. (1) In a hydrostatic drive device used in a high-pressure closed circuit, power loss occurs in both the hydraulic pump and the hydraulic motor, and a loss in the charging pump also occurs. Therefore, even if the respective efficiencies are combined under the best conditions, the upper limit of the power transmission efficiency of the entire apparatus is generally 80%, and when the discharge amount of the variable hydraulic pump is changed, the pump efficiency also changes. I do. Therefore, in a diesel engine of a diesel vehicle, when the rotation speed changes in a wide range from around the idle rotation to the rated rotation, the transmission efficiency decreases on the low rotation speed side, and the transmission efficiency is generally low.

(2) A hydraulic pump is used as a drive source. In order to perform a hydrostatic drive, for example, a pipe for connecting a hydraulic pump and a hydraulic motor, a rubber hose, and a hydraulic device are filled with pressurized oil. It is necessary to install a charging pump, a filter for removing contaminants of hydraulic oil in the hydrostatic circuit, and the like. (3) Since it is always used at a high pressure of 200 kg / cm ² or more, it is necessary to carefully check pipes and rubber hoses for cracks and damage, and check for contaminants in hydraulic oil.
Work time is required for daily maintenance and inspection.

[0007]

SUMMARY OF THE INVENTION The present invention eliminates the above disadvantages and has a simple and compact structure.
It is an object of the present invention to provide an accessory drive device for a diesel vehicle with high power transmission efficiency.

[0008]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides an auxiliary drive device for a diesel vehicle, comprising: an input shaft connected to a diesel engine having a variable rotation speed; And a high speed slip clutch or a low speed slip clutch connected via gears to the output side of the direct connection clutch or the output side of the one-way clutch, and the output side of each slip clutch. The clutch includes an auxiliary device to be connected and operating means for each of the slip clutches, and engages and disengages each clutch according to a change in input from the input shaft, thereby improving power transmission efficiency.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The principle of the present invention and a specific example thereof will be described below based on an accessory driving device shown in the drawings.

According to the principle of the present invention, a plurality of known slip clutches are disposed between an input shaft and an output side of a drive device, and each of the slip clutches is selectively or selectively operated according to a change in the rotation speed of the input shaft. It automatically engages and disengages, and keeps the rotation speed of the drive shaft of the auxiliary equipment, for example, the generator constant, and tries to obtain high transmission efficiency even when the fluctuation range of the rotation speed of the input shaft is wide. Things.

That is, transmission efficiency (η) = (output power / input power) × 100
(%) Since the input side of the slip clutch and the torque of the output side are equal, expressed by the output power = α × N _o × T input power = α × N _i × T. Where α is a coefficient, N
Represents the rotation speed, and T represents the transmission torque. Accordingly, the transmission efficiency (η) of the slip clutch is η = (N _o / N _i ) × 100% (a) where, N _o is the slip clutch output side rotation speed, and N _i is the input of the slip clutch. N _i > N _o because the clutch is slipping and rotating at the side rotation speed.

[0012] (a) As is apparent from the equation, if maintaining the output shaft speed N _o of the slip clutch constant, transmission efficiency of the slip clutch in proportion to the increase of the input rotational speed N _i decreases. On the basis of this characteristic, the accessory drive device according to the present invention is provided with a plurality of slip clutches, and is used while switching only in a range where the slip ratio is as small as possible and the transmission efficiency is high, and the fluctuation range of the input shaft speed is limited. Even in a wide case, high transmission efficiency can be obtained. Note that the number of slip clutches and the number of times of switching are set to the minimum necessary.

FIG. 1 shows a diesel engine accessory drive apparatus according to an embodiment of the present invention, which includes an input shaft 1 connected to a diesel engine (not shown), and a hydraulic multi-disc type provided on the input shaft 1. Direct coupling 2 and one-way clutch 3
And The input side member of the direct connection clutch 2 is fixed to the input shaft 1, and the output side member is a high speed step slip clutch 5.
Has a directly connected gear 4 that meshes with the high-speed pinion 6.
The one-way clutch 3 has a large number of cams arranged between the inner ring and the outer ring, transmits torque from the inner ring side to the outer ring side, and turns freely in the opposite direction, and is a commercially available product. The inner ring is fixed to the input shaft 1, and the outer ring has a directly connected pinion 7.

The high-speed step-slip clutch 5 is provided on an intermediate shaft 8 parallel to the input shaft 1, and a high-speed pinion 6 and an intermediate gear 9 constituting an input-side member are integrally formed, and are directly connected to the direct-connect gear 4 and the direct-connect gear, respectively. It is in mesh with the pinion 7. The output side member has a drive gear 10 integrally formed and is fixed to the intermediate shaft 8. The drive gear 10 meshes with a driven gear 13 fixed to a generator drive shaft 12 of a generator 11, which is an auxiliary machine, and drives the generator 11 when the engine speed is high.

A low-speed gear 14 formed integrally with the intermediate gear 9 meshes with a low-speed pinion 16 of the input side member of the low-speed step slip clutch 15, and the low-speed step clutch 15
Drives the generator 11 when. Since the gear ratio between the drive gear 10 and the driven gear 13 is set to 1.0, the rotation speeds of the generator drive shaft 12 and the intermediate shaft 8 are the same. A fixed displacement lubricating pump 47 for supplying lubricating oil to the clutches and bearings of the accessory drive device is connected to the shaft end of the intermediate shaft 8, and the high-speed slip clutch 5 or the low-speed slip clutch When 15 operates, the lubricating oil pump 47 is driven. That is, when the generator 11 is driven, the lubricating oil pump 47 is always driven at the same speed as the generator 11.

Hereinafter, the power transmission path will be described.
First, when the rotation speed of the input shaft 1 is between N1 and N2 (see FIG. 5), the input shaft 1 is driven at the first speed increase ratio. For example,
N1 = 700, N2 = 894, 1st speed increase ratio = 1.766. The power transmission path is as follows: input shaft 1 → direct coupling 2 (on) → direct coupling 4 → high speed pinion 6 → low speed gear 1
4 (High-speed slip clutch is off) → Low-speed pinion 16 →
The low speed slip clutch 15 (slip engagement) → the generator drive shaft 12 and the intermediate shaft 8 → the AC generator 11 and the lubricating oil pump 47. The speed increase ratio due to the meshing between the direct connection gear 4 and the high speed pinion 6 is 1.045, and the speed increase ratio due to the meshing between the low speed gear 14 and the low speed pinion 16 is 1.690.
, The first speed increase ratio is 1.766 as described above.
become. Further, the speed increase ratio of the direct coupling pinion 7 and the intermediate gear 9 meshing with the direct coupling pinion 7 is set to 0.804, which is set smaller than the speed increasing ratio of the direct coupling gear 4 driven by the direct coupling clutch 2. At the time of the connection, the rotation speed of the one-way clutch 3 on the outer wheel side becomes larger than that of the inner wheel side, and no torque is transmitted from the one-way clutch 3.

Next, when the rotation speed of the input shaft 1 is at N2 and N3 (see FIG. 5), the input shaft 1 is driven at the second speed increase ratio. The power transmission path is as follows: input shaft 1 → (direct coupling clutch is off) one-way clutch 3 → direct coupling pinion 7 → intermediate gear 9 → low speed gear 14 (high speed slip clutch is off) → low speed pinion 16 → low speed slip clutch 15 (slip) Engagement) → the generator drive shaft 12 and the intermediate shaft 8 → the generator 11 and the lubricating oil pump 47. The high-speed pinion 6 and the intermediate gear 9
And the low-speed gear 14 are integrally formed, rotatably supported on the intermediate shaft 8, and provided with a spline at one end.
The steel plate of the high speed slip clutch 5 is engaged.

Further, when the rotational speed of the input shaft 1 is at N3 and N4 (see FIG. 5), the input shaft 1 is driven at the third speed increase ratio.
Power transmission path is from input shaft 1 → direct coupling clutch 2 (on) →
Directly connected gear 4 → high speed pinion 6 → high speed step slip clutch 5
(Slip engagement) → drive gear 10 and intermediate shaft 8 → driven gear 13 and lubricating oil pump 47 → generator drive shaft 12 →
The generator 11.

Further, when the rotation speed of the input shaft 1 is equal to or higher than N4 (see FIG. 5), the input shaft 1 is driven at the fourth speed increase ratio. Power transmission path is input shaft 1 → one-way clutch 3
→ Directly connected pinion 7 → Intermediate gear 9 → High-speed stepping clutch 5
(Slip engagement) → drive gear 10 and intermediate shaft 8 → driven gear 13 and lubricating oil pump 47 → generator drive shaft 12 →
The generator 11.

FIG. 2 shows the configuration of a cross section of the low-speed stepping clutch 15. The extension 18 of the low-speed pinion 16 that constitutes the input member of the low-speed stepping clutch 15 includes:
A spline 19 is formed on the outer periphery, and an annular steel plate 20 having a spline engagement portion formed on the inner periphery is engaged with the spline 19. On the other hand, a spline 22 is formed on the inner periphery of the hollow portion of the cylindrical extension 21 of the driven gear 13 which is the output side member, and an annular friction plate 23 having a spline engagement portion formed on the outer periphery is formed of the steel plate 20. And are alternately arranged. An annular piston chamber 24 is formed in the hollow portion of the output-side member.
6 are slidably disposed so as to sandwich the steel plate 20 and the friction plate 23 therebetween. Therefore, the clutch hydraulic oil from the clutch hydraulic oil pump 17 (arrow W)
When the clutch piston 25 moves due to the pressure of the low speed pinion 16 and the driven gear 13, the steel plate 20 and the friction plate 23 are pressed against the clutch piston 25 and the back plate 26 fixed to the output side member. Can be transmitted to the motor. In addition,
Arrow V indicates the flow direction of the lubricating oil supplied to the plate portion. The direct connection clutch 2 and the high-speed stepping clutch 5 have the same configuration.

FIG. 3 shows a hydraulic circuit which is an operating means of each of the clutches 2, 5 and 15 (all clutches are shown in a disengaged state in the figure). First, the oil pumped from the sump tank 27 provided in the auxiliary device driving device by the clutch hydraulic oil pump 17 is supplied to the clutch hydraulic pressure adjusting valve 28 at a constant pressure (here, about 20 kg).
/ Cm ² ). The pressure is adjusted to engage the proportional solenoid valve 29 and the direct-coupled clutch 2, and is sent to a clutch engagement / disengagement valve 30 which is disengaged, branched in the middle, and sent to a preload adjustment valve 32 via an orifice 31. The drain of the clutch oil pressure adjusting valve 28 is a lubricating oil pressure adjusting valve (not shown) of 2-3.
It is adjusted to kg / cm ² and supplied as lubricating oil for clutches, gears, bearings and the like. Further, the drain of the preload adjusting valve 32 is returned to the sump tank.

To the piston chamber 24 (FIG. 2) of each clutch, a slight pressure oil (for example, 1-2 kg / cm ² ) regulated by the preload regulating valve 32 is supplied when the clutch is disengaged. The piston 25 is maintained at the position immediately before pressing the plates 20, 23. For this,
As soon as the clutch engagement / disengagement valves 30, 33, 34 are turned on, the press-contact of the clutch plates 20, 23 is started, and the clutch can be switched quickly without any time loss at the time of clutch switching.

Direct coupling clutch 2, low speed slip clutch 15
The high-speed step-slip clutch 5 can be switched in conjunction with a change in the rotational speed of the diesel engine. As shown in FIG. 3, a controller 35 and an auxiliary drive shaft rotational speed sensor connected to the controller 35 are connected. 37,
A control means including a rotation speed setting device (not shown) is provided.
Is compared with the signal from the auxiliary drive shaft rotation speed detection sensor 37, and the difference is provided to the proportional solenoid valve 29 with a PI-adjusted correction signal, whereby the operating oil pressure of the slip clutch is adjusted to a pressure corresponding to the set rotation speed. To the auxiliary equipment, for example, the generator 11
Can be kept constant.

As shown in FIG. 4, an engine speed detection sensor 36 is connected to the controller 35, and signals from the engine speed detection sensor 36 are set to predetermined engine speeds N _I , N _2, when it is N ₃ or N ₄ is turned on, giving an oFF signal to the clutch Hamadatsuben 30, 33 and 34, by which, the speed increasing ratio corresponding to changes in the engine rotational speed is selected, the auxiliary machine, For example, the generator 11 is driven in a range where the slip ratio is small.

That is, (1) the engine speed sensor 3
6 detects that the engine speed has reached N ₁ , an ON signal is output from the controller 35 to the solenoids of the clutch engagement / disengagement valves 30 and 34, and the direct coupling clutch 5 and the low speed step sliding clutch 15 are connected. At the same time, the controller 35 compares the rotation speed setting signal 38 (for example, set to 1200 rpm) from the rotation speed setting device with the rotation speed detection signal of the generator drive shaft, and proportionally corrects the difference by PI adjustment. This is given to the solenoid of the solenoid valve 29. Thus, the clutch operating oil pressure supplied to the piston chamber of the low-speed stepping clutch 15 is set at 1200 rpm, which is the set pressure.
, And the number of revolutions of the generator 11 is always kept constant, so that electric power of a constant frequency is obtained.

Further, since the rotation speed of the generator drive shaft 12 is maintained at a constant value, the rotation speed of the intermediate shaft 8 in conjunction therewith is also maintained at a constant value, and the lubricating oil pump 47 connected to the intermediate shaft 8 is In addition, a constant discharge amount is always supplied without being affected by changes in the engine speed. In general, a fixed displacement pump displacement driven by an engine whose rotational speed changes is selected so that the required discharge rate is secured even when the engine speed changes to the minimum side. Is changed to the maximum side, the discharge amount becomes more than necessary, and the excess amount is returned to the tank without being used. For this reason, when the engine speed changes in a wide range from the idle speed to the rated speed, about 40% of the discharge amount becomes excess at the rated speed, which leads to an increase in the pump driving force. According to the drive device of the present invention, the pump is always driven at a constant rotation speed without being affected by a change in the engine rotation speed, so that the pump discharge amount per rotation, that is, the size of the pump is reduced. And the driving force of the pump is small.

(2) When the engine speed sensor 36 detects that the engine speed has reached N ₂ , an off signal is output to the solenoid of the clutch on / off valve 30, and the direct coupling clutch 2 is disconnected. The one-way clutch 3 is automatically engaged, and the speed of the generator drive shaft 12 is maintained constant by the low-speed step-slip clutch 15 as described above.

(3) When the engine speed sensor 36 detects that the engine speed has reached N ₃ , an ON signal is output to the solenoids of the clutch on / off valves 30 and 33, and the direct connection clutch 2 and the high speed While the slip clutch 15 is connected, an off signal is output to the solenoid of the clutch on-off valve 34, and the low speed slip clutch 15 is disconnected. Then, the rotation speed of the generator drive shaft 12 is kept constant by the high-speed step slip clutch 15 as described above.

[0029] (4) the engine rotational speed sensor 36 detects that the engine speed has reached N _4, OFF signal is outputted to the solenoid of the clutch Hamadatsuben 30, direct clutch 2 is interrupted, The one-way clutch 3 is automatically engaged, and the rotational speed of the generator drive shaft 12 is kept constant by the high-speed step-slip clutch 5 as described above. As described above, the control unit including the controller 35 automatically switches the speed increase ratio in accordance with the change in the engine speed, and can control the slip ratio of each slip clutch to fall within a predetermined range. .

FIG. 4 tabulates the above description, and FIG. 5 shows the transmission efficiency corresponding to the engine speed in FIG. In FIG. 5, X indicates a change in transmission efficiency in the accessory drive device according to the present invention, and Y indicates a change in transmission efficiency in the conventional hydrostatic drive device. That is,
The power transmission efficiency of the accessory drive device according to the present invention is 74 to
In the range of 95%, the transmission efficiency is higher than that of the conventional hydrostatic drive at almost all engine speeds except a part of the engine speed.

In the embodiment of the present invention shown in FIG. 6, the second gear 4 meshes with the first gear 39 integrally connected to the input side member of the direct coupling clutch 2 fixed to the input shaft 1.
0 is provided on a second accessory drive shaft 41 parallel to the input shaft 1, and a first compressor 42 as an accessory is provided so as to be driven by one end of the accessory drive shaft 41. Also,
When the fourth gear 44 fixed to the third auxiliary drive shaft 45 parallel to the second auxiliary drive shaft 41 is engaged with the third gear 43 of the second auxiliary drive shaft 41, the third auxiliary drive shaft is engaged. 45 is driven, and the second compressor 46 connected to one end thereof and the clutch hydraulic oil pump 17 connected to the other end thereof are driven. The first and second compressors 42, 4
6 may be a single large-capacity unit because of the vehicle and installation space, and since no cooling device is required in winter, there is no need to use a compressor. Equipped with an electromagnetic clutch,
It is preferable to shut off when not in use. Pressure oil from the clutch hydraulic oil pump 17 is supplied to the piston chamber of each hydraulic clutch to connect the clutches.

FIG. 7 shows an external view of an accessory driving device according to another embodiment of the present invention, in which the generator 11 is driven at a constant speed and the blower 48 is driven by the electric power. I have. The power of the diesel engine E is transmitted to the input shaft 1 of the accessory drive device via the elastic joint C and the universal joint J. Part of the electric power generated by the electric motor 11 is sent to the electric motor 49 to drive the blower 48 and send air to the cooling device 50. The cooling device 50, that is, the radiator is supplied with cooling water for cooling the diesel engine. Since the amount of heat exchange in the cooling device greatly varies depending on the outside air, energy can be further saved by automatically controlling the number of revolutions using a variable speed motor by an inverter. As can be seen from the figure, in this example, since there is no hydrostatic drive, there is no piping and hydraulic equipment involved, and the overall configuration is simplified.

FIG. 8 shows an external view of an accessory driving device according to still another embodiment of the present invention, in which the AC generator 11 is driven at a constant speed and only the blower 48 of the cooling device is driven by hydrostatic pressure. An example is shown. That is, the variable displacement hydraulic pump 51 is driven from the end of the input shaft 1, the fixed displacement hydraulic motor 52 is attached to the blower 48 for the cooling device 50, and both are connected by the closed circuit 53, and the It is what constituted. With respect to fluctuations in the number of revolutions of the input shaft 1, the swash plate angle of the hydraulic pump 51 is adjusted to secure a required discharge amount, and the hydraulic motor 52, that is, the required power of the blower 48 is maintained. Note that this hydrostatic drive portion is the known method described above. In this example, only the blower uses a hydrostatic drive, so some piping etc. is required,
In addition to reducing the number of pipes compared to known methods,
There is an advantage that the capacity of the generator can be reduced. Note that the transmission efficiency is reduced by the use of the hydrostatic drive.

Although the above description has been made with reference to a four-speed type accessory drive device, a six-speed type accessory drive device is also possible. For example, as shown in FIG. 9, in the accessory driving device shown in FIG. 1, the output side member of the direct coupling clutch 2 is provided with the second one-way clutch 54 and the second direct coupling clutch 57, and the second one-way clutch 53 The outer ring is provided with a second directly-connected gear 55 that meshes with the second high-speed pinion 56 of the high-speed stepping clutch 5. The output member of the second direct coupling clutch 57 is provided with a first direct coupling gear 4a that meshes with the first high speed pinion 6a of the high speed step sliding clutch 5. This 6-speed type accessory drive device
The range of change in engine speed is wide, and the efficiency is reduced in the 4-speed type. The range of change in engine speed is not so wide, but the loss horsepower of the slip clutch is further reduced, and the accessory drive device is reduced. It is suitable for improving the transmission efficiency of the transmission.

[0035]

According to the present invention, a hydrostatic multi-plate direct-coupled clutch and a one-way clutch provided on an input shaft of an accessory drive device, and a low-speed step-slip connected to the output side of the direct-coupled clutch via a gear. Each of the slip clutches comprises a clutch, a high-speed slip clutch connected to the output side of the one-way clutch via a gear, an auxiliary device connected to the output side of each slip clutch, and an operating means for each clutch. Less slip and power transmission efficiency increases,
To that extent, the output of the diesel engine can be used as the acceleration power of the vehicle, and the acceleration of the vehicle can be improved. In addition, the hydraulic drive part can be eliminated or minimized, the entire accessory drive device can be simplified, and maintenance and inspection work can be facilitated.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram of an accessory drive device for a diesel vehicle according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view of a low-speed stepping clutch of the accessory driving device of FIG. 1;

FIG. 3 is an explanatory diagram of operating means of each slip clutch of the accessory driving device of FIG. 1;

FIG. 4 is an explanatory view showing an operation of each sliding clutch of FIG. 3 by operating means.

FIG. 5 is a table showing the power transmission efficiency of the accessory drive device of the present invention in comparison with a conventional hydrostatic power transmission efficiency.

FIG. 6 is an explanatory view of an accessory drive device for a diesel vehicle according to another embodiment of the present invention.

FIG. 7 is a schematic view showing the appearance of an accessory drive device for a diesel vehicle according to still another embodiment of the present invention.

FIG. 8 is a schematic diagram showing the appearance of an accessory drive device for a diesel vehicle according to still another embodiment of the present invention.

FIG. 9 is an explanatory diagram of a six-speed type accessory drive device according to an embodiment of the present invention.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 direct-coupled clutch 3 one-way clutch 4 direct-coupled gear 5 high-speed step-slip clutch 6 high-speed pinion 7 direct-coupled pinion 8 intermediate shaft 9 intermediate gear 10 drive gear 11 generator 12 generator drive shaft 13 driven gear 14 low-speed gear 15 low-speed step slide Clutch 16 Low speed pinion 17 Clutch hydraulic oil pump 24 Piston chamber 25 Clutch piston 30, 33, 34 Clutch disengagement valve 35 Controller 36 Engine speed sensor 37 Auxiliary drive shaft speed sensor 42 First compressor 46 Second compressor 47 Lubricating oil pump 48 Blower 49 Motor 50 Cooling device 51 Variable displacement hydraulic pump 52 Fixed displacement hydraulic motor 53 Closed circuit 54 Second one-way clutch 55 Second directly-coupled gear 56 Second high-speed pinion 57 Second directly-coupled clutch

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yuichiro Kaneko Saitama Prefecture Kumagaya City, No. 815 No. 75, No. 75 (72) Inventor Hidemi Naito 486-8, Shimojo Koka, Oji, Kamo City, Niigata Prefecture (72) Inventor Matsuoka Nariyasu 2-4-24 Shibata, Kita-ku, Osaka-shi, Osaka West Japan Railway Company (72) Inventor Mikito Sekiya 2-4-2-24, Shibata, Kita-ku, Osaka-shi, Osaka West Japan Railway Company F Terms (Reference) 3D037 CA02 CA08 CB06 CB07 CB13 CB36

Claims (6)

[Claims] An input shaft connected to a diesel engine having a variable speed, a hydraulic multi-plate type direct coupling clutch and a one-way clutch provided on the input shaft, and an output side of the direct coupling clutch or an output side of the one-way clutch. A high speed slip clutch or a low speed slip clutch connected via gears, an auxiliary device connected to the output side of each slip clutch, and an operating means for each slip clutch, and a variation in input from the input shaft. An auxiliary drive device for a diesel vehicle, wherein each clutch is disengaged and disengaged in accordance with the condition, thereby improving power transmission efficiency. 2. The accessory drive device for a diesel vehicle according to claim 1, wherein said clutch operating means has clutch operating oil control means. 3. The accessory drive device for a diesel vehicle according to claim 1, wherein the accessory is a generator. 4. The accessory drive device for a diesel vehicle according to claim 1, wherein the accessory is a generator, and a blower of the cooling device is driven by the generator. 5. The accessory drive device for a diesel vehicle according to claim 1, wherein the accessory is a generator and a fixed displacement hydraulic pump. 6. The diesel engine according to claim 3, wherein a variable displacement hydraulic pump for driving a hydraulic motor is provided at a shaft end of the input shaft, and a blower of a cooling device is driven by the hydraulic motor. Auxiliary equipment drive for moving vehicles.