JP2003028033A - Starter for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a starter for an internal combustion engine capable of preventing increase of friction rotation resistance and abrasion of a brush of an electric motor, and executing a start in one of a hydraulic actuator and the electric motor without trouble even if either of the hydraulic actuator and the electric motor is in an inoperable state. SOLUTION: This starter has the hydraulic actuator 15; a first rotary shaft 15a rotationally driven by the hydraulic actuator 15; the electric motor 17; a second rotary shaft 17a disposed in parallel with the first rotary shaft 15a and rotationally driven by the electric motor 17; a driven gear 14 rotating together with a crankshaft 2; a driving gear 12 meshing with the driven gear 4 at the start-up time; a third rotary shaft 13 connected to the driving gear 12; a first power transmission mechanism 19 connecting the first and third rotary shafts 15a, 13 such that the first and third rotary shafts 15a, 13 can be cut off from each other and transmitting rotation of the first rotary shaft 15a to the third rotary shaft 13; and a second power transmission mechanism 21 connecting the second and third rotary shafts 17a, 13 such that the second and third rotary shafts 17a, 13 can be cut off form each other and transmitting rotation of the second rotary shaft 17a to the third rotary shaft 13.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine starter for starting an internal combustion engine with a hydraulic actuator and an electric motor.

[0002]

2. Description of the Related Art As a conventional starting device of this type, for example, one described in Japanese Utility Model Laid-Open No. 59-73579 is known. The starting device has an electric motor and a hydraulic motor, and is configured to start an internal combustion engine (hereinafter referred to as “engine”) by using both motors. The electric motor has a pinion splined to its rotary shaft, and at the time of starting, the pinion slides axially toward the engine side by a plunging mechanism and meshes with a ring gear integral with the crankshaft of the engine. It On the other hand, the hydraulic motor is arranged on the opposite side of the rotary shaft of the electric motor from the pinion, and is connected in series on the same axis of the rotary shaft via a one-way clutch.
The hydraulic motor is driven by the hydraulic pressure accumulated in the accumulator, and the operation / stop of the hydraulic motor is controlled by opening / closing an electromagnetic opening / closing valve provided between the hydraulic motor and the accumulator in accordance with the hydraulic pressure in the accumulator.

In this starting device, at the time of starting, the pinion of the electric motor is engaged with the ring gear by the jumping mechanism, and the hydraulic motor is driven when the hydraulic pressure in the accumulator is equal to or higher than a predetermined value. As a result, the rotation of the hydraulic motor is transmitted to the rotating shaft of the electric motor via the one-way clutch, and further transmitted from the pinion to the ring gear, whereby the engine is started.
On the other hand, when the hydraulic pressure in the accumulator is less than the predetermined value, the hydraulic motor is stopped and the electric motor is driven to start the engine.

[0004]

However, in this conventional starting device, the hydraulic motor is connected in series to the electric motor. Therefore, when starting with the electric motor, the one-way clutch idles to prevent the hydraulic pressure from increasing. While the rotation of the electric motor is not transmitted to the motor, when starting with the hydraulic motor, the rotation is transmitted to the electric motor through the one-way clutch, and the electric motor rotates together with the hydraulic motor at the same number of rotations. I will end up. Therefore, there is a problem that the brush that is constantly in contact with the rotating shaft of the electric motor is easily worn. The problem of brush wear is that the high torque characteristics of the hydraulic motor are used to apply the restart at idle stop. This is especially noticeable as the number increases. When the brush wears, the rotational resistance due to friction increases, and the torque transmission efficiency of the hydraulic motor to the engine side decreases, which adversely affects the startability and increases the output of the hydraulic motor. Need to be designed.

In addition, the electric motor must be designed to have a robust structure so that it can withstand a high speed as the starting speed of the hydraulic motor increases, although it is not necessary for the original starting. However, it causes extra cost increase. Further, when the electric motor becomes inoperable due to sticking of foreign matter or the like, the hydraulic motor cannot be started, and as a result, the electric motor cannot be started at all.

The present invention has been made in order to solve such a problem, and can prevent abrasion of a brush of an electric motor, which is caused by combined use with a hydraulic actuator, and increase in frictional rotation resistance due to the abrasion of the brush. An object of the present invention is to provide a starting device for an internal combustion engine, which can start the engine without any trouble even if one of the actuator and the electric motor becomes inoperable.

[0007]

In order to achieve this object, the invention according to claim 1 of the present invention is a starting device for an internal combustion engine for starting the internal combustion engine 1 by rotationally driving a crankshaft 2. A hydraulic actuator driven by hydraulic pressure (the hydraulic motor 15 in the embodiment (hereinafter the same in this section)), a first rotary shaft (rotary shaft 15a) rotationally driven by the hydraulic actuator, and an electric motor (electric motor 17). ), And is arranged in parallel to the first rotation axis,
The second rotary shaft (rotary shaft 17) driven to rotate by an electric motor.
a), a driven gear (ring gear 4) that rotates integrally with the crankshaft 2, a drive gear (pinion gear 12) that meshes with the driven gear when the internal combustion engine 1 is started, and a third rotating shaft connected to the drive gear. (Output shaft 13) and first and third
The first power transmission mechanism (first one-way clutch 19) for connecting the rotation shafts of the first rotation shaft to each other in a disconnectable manner and transmitting the rotation of the first rotation shaft to the third rotation shaft, and disconnecting the second and third rotation shafts from each other A second power transmission mechanism (second one-way clutch 2) that is operably connected and transmits the rotation of the second rotation shaft to the third rotation shaft.
1) and are provided.

In this internal combustion engine starter, the first rotary shaft which is rotationally driven by the hydraulic actuator and the second rotary shaft which is rotationally driven by the electric motor are arranged in parallel with each other. The first rotating shaft is disconnectably connected to the third rotating shaft to which the drive gear is connected by the first power transmission mechanism,
The second rotary shaft is disconnectably coupled to the third rotary shaft by the second power transmission mechanism. Then, at the time of starting by the hydraulic actuator, the hydraulic actuator is driven with the drive gear meshing with the driven gear integrated with the crankshaft, the first power transmission mechanism in the connected state, and the second power transmission mechanism in the disconnected state. To be done. Accordingly, the rotation of the hydraulic actuator is transmitted to the third rotation shaft via the first rotation shaft and the first power transmission mechanism, and further transmitted to the driven gear via the drive gear, so that the internal combustion engine is It is started. In this case, since the second rotary shaft is blocked from the third rotary shaft by the second power transmission mechanism, the power of the internal combustion engine and the hydraulic actuator is not transmitted to the electric motor at all, and the electric motor is rotated. Also, it does not become a rotational resistance.

On the other hand, at the time of starting by the electric motor, the drive gear meshes with the driven gear, and conversely to the above, the first gear is engaged.
The electric motor is driven with the power transmission mechanism in the cutoff state and the second power transmission mechanism in the connected state. Accordingly, the rotation of the electric motor is transmitted to the third rotation shaft via the second rotation shaft and the second power transmission mechanism, so that the internal combustion engine is started. In this case also, since the first rotary shaft is blocked from the third rotary shaft by the first power transmission mechanism, the power of the internal combustion engine and the electric motor is not transmitted to the hydraulic actuator, and the hydraulic actuator rotates. It is not made to act and it does not become a rotational resistance.

As described above, according to the starting device of the present invention, the power of the hydraulic actuator and the electric motor is selectively transmitted to the internal combustion engine in a state where the power transmission between the hydraulic actuator and the electric motor is cut off, and the internal combustion engine is started. You can That is, in the case of starting by either the hydraulic actuator or the electric motor, the starting can be performed independently of each other without rotating the other at all. As a result, it is possible to prevent abrasion of the brush of the electric motor, which is caused by the combined use with the hydraulic actuator, and increase in frictional rotation resistance due to the abrasion. In addition, extra design such as making the electric motor robust is not necessary according to the high rotation characteristics of the hydraulic actuator. Further, even when one of the hydraulic actuator and the electric motor is in an inoperable state, the other can start the engine without any trouble.

According to a second aspect of the present invention, in the internal combustion engine starting device according to the first aspect, the first and second power transmission mechanisms have the first and second rotating shafts driving the third rotating shaft. The first and second one-way clutches 19 and 21 that transmit the rotations of the first and second rotating shafts to the third rotating shaft only when rotating in the rotating direction are characterized by being respectively configured.

According to this structure, at the time of starting by the hydraulic actuator, the rotation of the first rotary shaft is transmitted to the third rotary shaft via the first one-way clutch, while at the same time,
Since the second one-way clutch idles, the second and third rotating shafts are in the cutoff state. On the other hand, at the time of starting by the electric motor, contrary to the above, the rotation of the second rotary shaft is the second
It is transmitted to the third rotating shaft through the one-way clutch, and the second and third wheels are driven by the idle rotation of the first one-way clutch.
The rotating shafts of the are cut off from each other. As described above, in the starting device of the present invention, the one-way clutch is used as each of the first and second power transmission mechanisms, so that when the hydraulic actuator or the electric motor is started, the disconnection state of the other can be made simple. , Can be easily realized without requiring any control.

[0013]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a starting device for an internal combustion engine according to a first embodiment of the present invention. Reference numeral 1 in the figure indicates an internal combustion engine (hereinafter referred to as "engine") (ENG).
The flywheel 3 is fixed to the crankshaft 2. Further, along the outer peripheral surface of the flywheel 3, along with this, a ring gear 4 composed of a helical gear is provided.
Are integrally formed.

On the other hand, the starting device 11 includes the ring gear 4
(Driven gear), pinion gear 12 (driving gear),
An output shaft 13 (third part, which has a pinion gear 12 connected to one end thereof)
(Rotating shaft) and the pinion gear 12 when the engine 1 is started.
The magnet switch (MG / SW) 14 for moving and engaging the ring gear 4 side, the hydraulic motor 15 (hydraulic actuator) that rotationally drives the pinion gear 12 at the time of starting, and the hydraulic motor drive mechanism 16 that drives the hydraulic motor 15. And an electric motor 17 (electric motor) for auxiliary drive
And an ECU 5 for controlling the operation of the hydraulic motor 15 and the like.

The pinion gear 12 is a helical gear that can mesh with the ring gear 4. The pinion gear 12 is fixed to one end of a pinion shaft 12a that is coaxially spline-coupled with the output shaft 13, and is thereby connected to the output shaft 13 such that it cannot rotate but is movable in the axial direction.

The magnet switch 14 is the plunger 1.
4a, and a solenoid having a built-in exciting coil, a return spring (neither is shown), and the like.
The plunger 14a is arranged coaxially with the output shaft 13. With the above configuration, the magnet switch 1
4, the plunger 14a faces the pinion shaft 12a of the pinion gear 12 with a space therebetween, so that the pinion gear 12 is held in a non-meshing position where it does not mesh with the ring gear 4 (state in FIG. 1). On the other hand, when the magnet switch 14 is excited, the plunger 14a projects and presses the pinion shaft 12a, so that the pinion gear 12 is driven to a meshing position where it meshes with the ring gear 4 (not shown).

The hydraulic motor 15 is of a swash plate type, for example, and is driven by the hydraulic pressure supplied from the hydraulic motor drive mechanism 16. The rotary shaft 15a (first rotary shaft) is
The rotary shaft 15a is arranged in parallel with the output shaft 13
Output gear 15b and intermediate gears 18a, 18b integrated with
Speed increasing gear train 18 and a first one-way clutch 1
It is connected to the output shaft 13 via 9 (first power transmission mechanism). This first one-way clutch 19 is driven only when the hydraulic motor 15 is driven and the output shaft 13 is driven.
The rotation is set to be transmitted, and the rotation is blocked when the rotation relation is opposite to this.

On the other hand, the electric motor 17 is the hydraulic motor 15
If the starting by is impossible or inappropriate, the hydraulic motor 15
The pinion gear 12 is driven to rotate instead of the
Is to assist the start of the. For example, when the engine 1 is in an extremely low temperature state, the friction is large, and the startability of the engine 1 is deteriorated. Therefore, it takes time to complete the start, whereas the hydraulic motor 1
Since the structure of No. 5 has a relatively short torque output time due to its structure, there is a possibility that stable starting cannot be ensured, so starting is performed by the electric motor 17. The rotating shaft 17a (second rotating shaft) of the electric motor 17 is the output shaft 13
A reduction gear train 20 that is disposed in parallel with the rotary shaft 15a of the hydraulic motor 15 and in parallel with the rotary shaft 17a, and includes an output gear 17b and intermediate gears 20a and 20b that are integral with the rotary shaft 17a.
And the second one-way clutch 21 (second power transmission mechanism)
Is connected to the output shaft 13 via. The second one-way clutch 21 is also set to transmit the rotation only when the electric motor 17 is driven and the output shaft 13 is driven.

The hydraulic motor drive mechanism 16 is composed of an oil pump 22, an electric motor 23 for accumulating pressure that drives the oil pump 22, an accumulator 24 that accumulates the hydraulic pressure boosted by the oil pump 22, and the like. The oil pump 22 is directly connected to the rotary shaft 23 a of the electric motor 23, and its suction port is connected to the reserve tank 25. The discharge port of the oil pump 22 has an oil passage 26.
Is connected to the inlet port 15c of the hydraulic motor 15 via the, and the oil passage 26 is provided with a check valve 27. Further, the branch passage 2 is provided from the downstream side of the check valve 27 of the oil passage 26.
6a is branched, and the accumulator 24 is provided in the branch pipe 26a. With the above configuration, the oil pump 22 is driven in accordance with the operation of the electric motor 23, and the hydraulic pressure increased by the oil pump 22 is sent to the accumulator 24 via the check valve 27 and accumulated therein.

The oil passage 26 also has an accumulator 24.
An electromagnetic switching valve 28 is provided between the hydraulic motor 15 and the hydraulic motor 15. The electromagnetic on-off valve 28 is a normally closed type,
That is, while the oil passage 26 is closed in the non-excited state, the oil passage 26 is opened when excited by the drive signal from the ECU 5, and the hydraulic pressure accumulated in the accumulator 24 is supplied to the hydraulic motor 15. The oil supplied to the hydraulic motor 15 is returned to the reserve tank 25 via the outlet port 15d and the return oil passage 29. Further, a hydraulic sensor 30 is provided on the branch path 26a. The pressure sensor 30 detects the hydraulic pressure POIL in the accumulator 24 and outputs the detection signal to the ECU 5.

The ECU 5 has an I / O interface, C
It is composed of a microcomputer including a PU, a RAM, a ROM (all not shown), and the like. ECU
5 outputs a drive signal to the magnet switch 14, the electric motors 17 and 23, and the electromagnetic on-off valve 28 in accordance with an operation state of an ignition key (not shown), a detection signal from the hydraulic pressure sensor 30, and the like. Control the behavior of.

Next, the operation of the starting device 11 having the above structure will be described. First, when the engine 1 is in operation, the hydraulic pressure PO in the accumulator 24 detected by the hydraulic pressure sensor 30.
When IL falls below the predetermined value POILL,
The electric motor 23 is driven and the oil pump 22 operates. As a result, the hydraulic pressure boosted by the oil pump 22 is accumulated in the accumulator 24. The predetermined value P
OILL is set as a hydraulic pressure value sufficient to drive the hydraulic motor 15, for example. Also, the hydraulic pressure POIL
Is a predetermined upper limit value POIL larger than the predetermined value POILL
When it reaches H, the electric motor 23 and the oil pump 22 are stopped. As described above, when the engine 1 is in operation, the hydraulic pressure POIL in the accumulator 24 is increased to a state sufficient to drive the hydraulic motor 15, and after the engine 1 is stopped, the check valve 27 changes the hydraulic pressure state. Maintained.

When the engine 1 is started by the hydraulic motor 15, the magnet switch 14 is driven to move the pinion gear 12 to the meshing position and mesh with the ring gear 4, and the electromagnetic opening / closing valve 28 is excited to excite the oil passage. Open 26. As a result, hydraulic pressure is supplied from the accumulator 24 to the hydraulic motor 15, and the hydraulic motor 15 is rotationally driven. The rotation of the hydraulic motor 15
After the speed is increased by the speed increasing gear train 18, the speed is transmitted to the output shaft 13 via the first one-way clutch 19, and the ring gear 4 is further rotated via the pinion gear 12, whereby the engine 1 is started. In this case, since the second one-way clutch 21 is provided between the output shaft 13 and the rotating shaft 17a of the electric motor 17, the power of the output shaft 13 is not transmitted to the electric motor 17 at all.

When the electric motor 17 is started,
The electromagnetic opening / closing valve 28 is held in a non-excited state, and the electric motor 17 is driven. The rotation of the electric motor 17 is
After the speed is reduced by the reduction gear train 20, it is transmitted to the output shaft 13 via the second one-way clutch 21, and the ring gear 4 is rotated to start the engine 1. In this case as well, the first shaft is placed between the output shaft 13 and the hydraulic motor 15.
Since the one-way clutch 19 is provided, the power of the output shaft 13 is not transmitted to the hydraulic motor 15 at all. Further, after the engine 1 is started and the rotational speed of the ring gear 4 exceeds the rotational speed of the pinion gear 12, only the output shaft 13 is operated by the first and second one-way clutches 19 and 21. Since the engine 1 runs idle, the power of the engine 1 is not transmitted to the hydraulic motor 15 or the electric motor 17 at all.

As described above, according to this embodiment, the rotary shaft 15a of the hydraulic motor 15 and the rotary shaft 1 of the electric motor 17 are rotated.
7a are arranged in parallel with each other and the hydraulic motor 15
The engine 1 is started by selectively transmitting the power of the electric motor 17 to the output shaft 13 by the first and second one-way clutches 19 and 21. Therefore, in the case of starting with either of the two motors 15 and 17, the engine 1 is started independently of each other without completely rotating the other with the power transmission between the two motors 15 and 17 completely cut off. can do. As a result, it is possible to prevent the abrasion of the brush of the electric motor 17 and the increase in the frictional rotation resistance resulting from the combined use with the hydraulic motor 15. Further, it is not necessary to make extra design such as making the electric motor 17 robust according to the high rotation characteristic of the hydraulic motor 15. Furthermore, the hydraulic motor 1
5 When one of the electric motor 17 and the electric motor 17 is inoperable or unsuitable, for example, when the electric motor 17 is inoperable due to sticking, or when starting by the hydraulic motor 15 is not suitable such as in an extremely low temperature state. However, the other can be started without any trouble.

Further, in this embodiment, the rotary shaft 15a of the hydraulic motor 15 and the rotary shaft 17a of the electric motor 17 are
Since it is connected to the output shaft 13 via the first and second one-way clutches 19 and 21, when one of the hydraulic motor 15 and the electric motor 17 is started, the interruption state of the other is controlled by a simple configuration. Can be easily implemented without any need for.

FIG. 2 shows a starting device according to a second embodiment of the present invention. In the following description, components that are the same as or equivalent to those in the first embodiment described above will be assigned the same reference numerals, and descriptions thereof will be omitted as appropriate. As shown in the figure, the starting device 31 of the present embodiment
Compared with the starting device 11 of the first embodiment, the first and second one-way clutches 19 and 21 are connected to the hydraulic motor 1
5 rotation shaft 15a and the electric motor 17 rotation shaft 17a
In addition, they are different in that they are arranged coaxially.

Specifically, the hydraulic motor 15 is of a higher rotation type (smaller size) than that of the first embodiment, and the first one-way clutch 19 provided on the rotating shaft 15a and It is connected to the output shaft 13 via a constant-speed gear train 32 composed of an output gear 32a integrated with it and an input gear 32b integrated with the output shaft 13. On the other hand, the rotating shaft 17a of the electric motor 17 includes a second one-way clutch 21 provided coaxially, and a reduction gear train 33 including an output gear 33a integral with the second one-way clutch 21, an intermediate gear 33b, and an input gear 33c integral with the output shaft 13. Through the output shaft 1
It is connected to 3. Other configurations are similar to those of the first embodiment.

Therefore, also in this embodiment, the power of the rotary shaft 15a of the hydraulic motor 15 and the rotary shaft 17a of the electric motor 17, which are arranged in parallel with each other, is generated by the first and second one-way clutches 19 and 21.
In the state where the power transmission between 5 and 17 is completely cut off, the power is selectively transmitted to the output shaft 13 to start the engine 1. Therefore, the same effects as those of the first embodiment described above can be obtained.

The arrangement of the magnet switch 14, the hydraulic motor 15 and the electric motor 17 with respect to the output shaft 13 is not limited to those shown in FIGS. 1 and 2, and various modes are possible. Although not shown, for example, the electric motor 17
Are arranged in a decelerating state coaxially with the output shaft 13 via a planetary gear set, and the magnet switch 1
4 may be arranged in parallel or coaxially with the output shaft 13. Alternatively, it is also possible to adopt a high rotation type motor as the hydraulic motor 15 and dispose it coaxially with the output shaft 13, thereby making the starter 11 more compact by omitting the speed increasing gear train 18. Can be configured.
Further, by adopting a low rotation / high output type electric motor 17 as well, it is possible to dispose the electric motor 17 coaxially with the output shaft 13 without a planetary gear set. It can be omitted.

FIG. 3 shows a starting device according to a third embodiment of the present invention. As shown in the figure, the starting device 41 of the present embodiment is different from the starting device 11 of the first embodiment,
The following points are different. That is, the rotating shaft 1 of the electric motor 17
7a is connected to the oil pump 22 via the first electromagnetic clutch 42. The rotary shaft 17 a of the electric motor 17 is the rotary shaft 1 of the output shaft 13 and the hydraulic motor 15.
The second electromagnetic clutch 43 (second power transmission mechanism) is arranged between the reduction gear train 20 and the output shaft 13 in parallel and in parallel with 5a, instead of the second one-way clutch 21 of the first embodiment. Is provided. With this, the first
The electric motor 23 dedicated to the pressure accumulation of the embodiment is omitted. The operations of the first and second electromagnetic clutches 42 and 43 are controlled by the ECU 5. Other configurations are similar to those of the first embodiment.

The operation of the starting device 41 is as follows. First, during operation of the engine 1, the second electromagnetic clutch 43 is held in the disengaged state, and when the hydraulic pressure POIL falls below a predetermined value POILL, the electric motor 17
And the first electromagnetic clutch 42 is connected. As a result, the rotation of the electric motor 17 is transmitted to the oil pump 22 via the first electromagnetic clutch 42, and the oil pump 22 is driven to accumulate pressure in the accumulator 24. When the hydraulic pressure POIL reaches the upper limit value POILH, the electric motor 17 is stopped and the first electromagnetic clutch 42 is disengaged. As described above, the hydraulic pressure P in the accumulator 24 is the same as in the starting device 11 of the first embodiment.
The OIL is maintained in a state sufficient to drive the hydraulic motor 15.

On the other hand, at the time of starting by the hydraulic motor 15,
Similar to the first embodiment, the magnet switch 14 is driven to excite the electromagnetic opening / closing valve 28, and the second electromagnetic clutch 43 is turned off. As a result, the engine 1 is started, and the power of the output shaft 13 is interrupted by the second electromagnetic clutch 43 and is not transmitted to the electric motor 17 at all. Also, at the time of starting by the electric motor 17,
By driving this and connecting the second electromagnetic clutch 43 while disconnecting the first electromagnetic clutch 42, the engine 1 is started without transmitting the rotation of the electric motor 17 to the oil pump 22 and the hydraulic motor 15. can do. Also in this case, the power of the output shaft 13 is
The hydraulic motor 1 is disengaged by the first one-way clutch 19.
No transmission to 5.

As described above, the starting device 41 of this embodiment is
According to the above, the second electromagnetic clutch 43 is used as the second power transmission mechanism for transmitting the power from the electric motor 17 to the output shaft 13, and the first one-way clutch 19 and the second electromagnetic clutch 19 are appropriately controlled by the ECU 5. 43 makes it possible to start the engine 1 in a state in which the power transmission between the two motors 15 and 17 is completely cut off.
And the effect of 2nd Embodiment can be acquired similarly.
Further, the single electric motor 17 can start the engine 1 and accumulate pressure in the accumulator 24. As a result, the starter 41 can be made compact and inexpensive as compared with the first embodiment which requires the two electric motors 17 and 23.

Although not shown, an electromagnetic clutch is used instead of the first one-way clutch 19 of this embodiment.
This may be controlled by the ECU 5. Alternatively, the first and second electromagnetic clutches 42, 4 of the present embodiment
Instead of 3, the third and second one-way clutches may be provided, respectively, and a reverse rotation circuit may be added to drive the electric motor 17 to rotate in a direction opposite to that at the time of starting. in this case,
The second one-way clutch is set to transmit the rotation to the output shaft 13 only when the electric motor 17 rotates normally, and the third one-way clutch is set to transmit the rotation to the oil pump 22 only when the electric motor 17 rotates in the reverse direction. It With the above configuration, it is possible to start the engine 1 and accumulate pressure in the accumulator 24 by rotating the electric motor 17 in the normal direction and in the reverse direction. That is, the power transmission mechanism is not limited to the one-way clutch or the electromagnetic clutch as long as the intermittent power supply can satisfy the requirements of the present embodiment.

Further, in the example of FIG. 3, the first electromagnetic clutch 42 and the oil pump 22 are arranged on the side opposite to the output shaft 13 of the electric motor 17, but the rotary shaft 17a and the output shaft 13 of the electric motor 17 are arranged. The oil pump 22 may be connected to an idler shaft that is arranged in parallel with the idler gear, and the idler gear and the idler shaft that mesh with the rotating shaft 17a and the output shaft 13 may be interrupted by the first electromagnetic clutch 42. With this configuration, when an idler gear is required in terms of space, it is possible to save space and share parts. In addition, the first electromagnetic clutch 42
The electric motor 17 and the electric motor 17 may be arranged coaxially.

Alternatively, the electric motor 17 is always connected to the oil pump 22, and the discharge passage of the oil pump 22 is connected to the accumulator 24 side and the reserve tank 25.
A flow path switching mechanism for switching to the side may be provided. With this configuration, pressure can be accumulated by driving the electric motor 17 and switching the discharge flow path of the oil pump 22 to the accumulator 24 side by the flow path switching mechanism. Further, at the time of starting the electric motor 17, the load of the electric motor 17 can be reduced by switching the discharge passage of the oil pump 22 to the reserve tank 25 side for relief. With this configuration, the power switching means such as the expensive first and second electromagnetic clutches 42 and 43 and the reverse rotation circuit in the third embodiment for sharing the electric motor 17 for starting and accumulating pressure is not required, and thus the cost is reduced. In addition, it is advantageous. Further, the flow path switching mechanism can be arranged separately from the starting mechanism such as the magnet switch 14 and the hydraulic motor 15, which is advantageous in layout.

FIG. 4 shows a starting device according to a fourth embodiment of the present invention. As shown in the figure, in the starting device 51 of the present embodiment, the check valve 27 and the electromagnetic opening / closing valve 28 are arranged in parallel with each other in the middle of the oil passage 26 that connects the inlet port 15c of the hydraulic motor 15 and the accumulator 24. It is provided, and the oil pump 22 of the first embodiment is omitted. The rotating shaft 17 a of the electric motor 17 is connected to the output shaft 13 via the planetary gear 52 and the second one-way clutch 21.

On the other hand, the rotary shaft 15a of the hydraulic motor 15 is
Through the first one-way clutch 19 and the starting gear train 54 including the output gear 19a integrated therewith, the intermediate gear 54a, and the gear 54b integrated with the output shaft 13, the output shaft 1
It is connected to 3. In addition, the rotary shaft 1 of the hydraulic motor 15
A gear 55a is provided at the end of 5a, and the pinion shaft 12
At the end opposite to the pinion gear 12 of a, the gear 55a
A gear 55b capable of meshing with is provided. These gears 55a and 55b constitute a pressure-accumulation gear train 55, which mesh with each other when the pinion gear 12 is in a non-meshing position with the ring gear 4 (state of FIG. 4), while
When the pinion gear 12 is in the meshing position, the meshing is disengaged.

The operation of the starting device 51 is as follows. First, at the time of starting by the hydraulic motor 15, the magnet switch 14 is driven and the electromagnetic opening / closing valve 28 is excited as in the first and third embodiments. As a result, the pinion gear 12 meshes with the ring gear 4, and the rotation of the hydraulic motor 15 is transmitted to the output shaft 13 via the first one-way clutch 19 and the starting gear train 54, whereby the engine 1 is started. In this case, as the pinion gear 12 moves to the meshing position, the pressure-accumulating gear train 55 is disengaged, so that the engine 1 is not started. Also, the hydraulic motor 1
The power of 5 is cut off by the second one-way clutch 21,
There is no transmission to the electric motor 17.

When the electric motor 17 is started,
The magnet switch 14 is driven, the electromagnetic opening / closing valve 28 is held in a non-excited state, and the electric motor 17 is driven. As a result, the rotation of the electric motor 17 is transmitted to the output shaft 13 via the planetary gear 52 and the second one-way clutch 21, whereby the engine 1 is started. In this case, due to the disengaged state of the pressure accumulating gear train 55 and the first one-way clutch 19, the power of the electric motor 17 is increased by the hydraulic motor 15.
Is never transmitted to.

On the other hand, when the engine 1 is in operation, the magnet switch 14 is deactivated, the electromagnetic opening / closing valve 28 is held in a non-excited state, and the hydraulic pressure POIL is set to a predetermined value POI.
When it falls below LL, the electric motor 17 is activated. As a result, the rotation of the electric motor 17 is transmitted to the output shaft 13 in the same manner as at the time of starting, and is further transmitted to the rotary shaft 15a of the hydraulic motor 15 via the gear train 55 for pressure accumulation in the meshed state. The rotation of this electric motor 17 is
The first one-way clutch 19 allows the starting gear train 5
4 is not transmitted to the hydraulic motor 15. Therefore, the hydraulic motor 15 is rotationally driven by the electric motor 17 via the pressure accumulating gear train 55. Further, since the starting gear train 54 and the pressure accumulating gear train 55 have one gear stage difference, the rotation direction of the rotary shaft 15 of the hydraulic motor 15 at this time is opposite to that at the time of starting. As a result, the hydraulic pressure boosted by the reverse rotation of the hydraulic motor 15 is changed to the inlet port 15
It is sent to the accumulator 24 via c, the oil passage 26 and the check valve 27, and the pressure is accumulated. Further, when the hydraulic pressure POIL reaches the upper limit value POILH, the electric motor 17 is stopped.

As described above, the starting device 51 of the present embodiment.
Also in the first and second one-way clutches 19,
With 21, the engine 1 can be started in a state in which the power transmission between the two motors 15 and 17 is completely shut off, and therefore, the effects of the first and second embodiments can be similarly obtained. The hydraulic motor 15 is driven in the forward direction by the hydraulic pressure in the accumulator 24 by the starting gear train 54 and the pressure accumulating gear train 55, and is driven by the electric motor 17 in the reverse rotation direction when the engine 1 is started. ,
It is possible to switch to a pressure accumulation state in which pressure is accumulated in the accumulator 24. As a result, the oil pump 22 for accumulating pressure in the first embodiment can be omitted, and the starter 51 can be correspondingly provided.
Can be made more compact and inexpensive. In addition, this embodiment does not require the power switching means such as the first and second electromagnetic clutches 42 and 43 used in the third embodiment for sharing the electric motor 17 for starting and accumulating pressure. Also in terms of cost, it is advantageous. In the present embodiment, the hydraulic motor 15 is used as an oil pump by rotating in the reverse direction.
As the hydraulic motor, for example, a swash plate type motor having a reversing mechanism may be adopted so that the hydraulic motor can be used as an oil pump without being reversely rotated. In that case, the intermediate gear 54a of the present embodiment for rotating the hydraulic motor 15 in the reverse direction is unnecessary, and the number of parts can be reduced accordingly.

[0044]

As described above, according to the internal combustion engine starter in accordance with the first aspect of the present invention, the power of the hydraulic actuator and the electric motor can be selectively supplied to the internal combustion engine in a state where the power transmission between them is cut off. Since it can be transmitted to the motor and it can be started, it is possible to prevent the abrasion of the brush of the electric motor due to the combined use with the hydraulic actuator and the increase in frictional rotation resistance due to it, and it is unnecessary to make extra design such as making the electric motor robust. At the same time, even if one of the hydraulic actuator and the electric motor is in an inoperable state, the other can start the engine without any trouble. Further, according to the starting device of the second aspect, by adopting one-way clutches as the first and second power transmission mechanisms respectively, when starting by one of the hydraulic actuator and the electric motor, the disconnection state of the other can be made simple. , Can be easily realized without requiring any control.

[Brief description of drawings]

FIG. 1 is a diagram showing a schematic configuration of a starting device for an internal combustion engine according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a schematic configuration of a starting device for an internal combustion engine according to a second embodiment of the present invention.

FIG. 3 is a diagram showing a schematic configuration of a starting device for an internal combustion engine according to a third embodiment of the present invention.

FIG. 4 is a diagram showing a schematic configuration of a starting device for an internal combustion engine according to a fourth embodiment of the present invention.

[Explanation of symbols] 1 Internal combustion engine 2 crankshaft 4 Ring gear (driven gear) 11 Starter 12 pinion gear (drive gear) 13 Output shaft (3rd rotating shaft) 15 Hydraulic motor (hydraulic actuator) 15a Rotary shaft of hydraulic motor (first rotary shaft) 17 Electric motor (electric motor) 17a Rotating shaft of electric motor (second rotating shaft) 19 1st one-way clutch (1st power transmission mechanism) 21 2nd one-way clutch (2nd power transmission mechanism) 31 Starter 41 Starter 43 Second electromagnetic clutch (second power transmission mechanism) 51 Starter

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Koichi Fushimi             1-4-1 Chuo Stock Market, Wako City, Saitama Prefecture             Inside Honda Research Laboratory

Claims (2)

[Claims] 1. A starting device for an internal combustion engine, which starts an internal combustion engine by rotationally driving a crankshaft, comprising: a hydraulic actuator driven by hydraulic pressure; and a first rotary shaft rotationally driven by the hydraulic actuator. An electric motor, a second rotary shaft that is arranged in parallel with the first rotary shaft and is rotationally driven by the electric motor, a driven gear that rotates integrally with the crankshaft, and the driven gear when the internal combustion engine is started. A drive gear meshing with the drive gear, a third rotary shaft connected to the drive gear, and the first and third rotary shafts so that they can be disconnected from each other, and the rotation of the first rotary shaft is transferred to the third rotary shaft. A first power transmission mechanism for transmitting the second power transmission mechanism, and a second power transmission mechanism for transmitting the rotation of the second rotation shaft to the third rotation shaft, the second power transmission mechanism connecting the second and third rotation shafts in a disconnectable manner. Equipment And starting system for an internal combustion engine, characterized in that are. 2. The first and second power transmission mechanisms,
First and second transmissions of the rotations of the first and second rotating shafts to the third rotating shaft only when the first and second rotating shafts rotate in a direction of driving the third rotating shaft. 2. The starting device for an internal combustion engine according to claim 1, wherein each of the one-way clutches is a starter.