Engine starting apparatus

Technical Field

The invention relates to a starting device for the engine of the following mechanism, when in the idling stop of the engine is still in inertial rotation of the rotary means in the process of transportation requirements of the engine under the condition of, in this kind of mechanism in the course of rotating the gear ring of the engine, the rotation of the motor of the pinion gear of the starter, the pinion gear and the ring gear of the engine, in addition the reversing can be engaged, by the re-starting time can be shortened.

Background Art

In the prior engine starting device in (hereinafter referred to as starter), in the engine stop state, to start action. Therefore, the pinion gear to the ring gear has not rotated is carried out under the state of engagement of the gear ring. However, in order to reduce fuel consumption and in the idle stop system, the rotation of the ring gear when the pinion gear meshes with the gear ring, in order to ensure that the starting sex.

For example, if the idle stop of the engine rotation has not stopped the moment the state of the input re-start-up under, or from a stopped state is re-started under the condition of shortening time required, is in the course of rotating the ring gear prior to the meshing of the pinion gear.

In this way, as the ring gear is meshed with the pinion gear in the course of rotating the method, the rotational speed of the ring gear to the synchronization of speed of the pinion of the starting motor is energized so as to carry out the method of meshing (for example with reference to Patent document 1). Furthermore, there are also used for synchronization in advance, through the arrangement of the mechanism, the friction mechanism in the utilization of the synchronous to a certain speed difference after the method of meshing the gear (for example, referring to Patent literature 2). Furthermore, there is also improved through the shape of the meshed with the pinion to be easier to method (for example, referring to Patent literature 3).

Literature of the prior art

Patent literature

Patent literature 1: Japanese Patent opens especially 2002-70699, the

Patent document 2: Japanese Patent opens especially 2006-132343, the

Patent literature 3 : opens especially Japanese Patent 2009-168230, the

However, in the prior art, there are the following technical problems.

After stopping of the engine ring gear because the inertial rotation and deceleration, but in this case, cause compression-expansion of the piston changes in torque generated by the fluctuation of the rotational speed on one side of the stop. Therefore, for example, Patent document 1 as shown, in order to use the engine to starting device (starter) the synchronous rotational speed of the ring gear and the pinion and the gear ring and the pinion gear, the need for complex structure. Specifically, the need to set up the access to or predicting the rotational speed of the ring gear and the pinion, and according to the control of the starter in order to make the gear ring and the pinion gear engages the complex structure.

In this kind of complex structure, the timing of the introduction of the pinion to rotate the pinion gear and the timing becomes important. However, even if the rotation of the pinion gear, the pinion gear to the increase in the rotation speed of the time also needs to the prescribed rotational speed. Furthermore, when the pinion gear is meshed with the gear ring when the push-out, also needs to be specified time. Furthermore, because of the time deviation, therefore, in fact, in the system in a simple, it is very difficult to the synchronous rotation speed of the engine to rotate the pinion gear, to make the pinion meshes with the gear ring.

Furthermore, if the engine speed of rotation very fast, the small gear is unable to keep pace with the rising of the rotational speed of the rotational speed of the engine, the pinion gear when the ring gear abuts, the phenomenon of reverse rotation of the ring gear will occur. In the case of reversal phenomenon, the need for reversal of rotation of engine, so that this kind of electric motor mode and control becomes complicated, it is very difficult to realize.

Furthermore, the fluctuation of the engine side inertial rotation in the way in the course of deceleration, according to the position of the piston before a stop of the engine and performs inversion. In order to enable the pinion to follow the reverse, the electric motor must also be reversed. In this case, because the motor and the performance of the control becomes complicated, therefore, in the simple system is very difficult to realize.

In this way, if the deviation of the actually produced, and the like taken into account, only in a certain limit under the condition of, we can make the engaged speed synchronous for engagement.

On the other hand, for example, Patent literature 2 as shown, the prior use of synchronizing mechanism through the rotate at the same speed to the pinion gear and the ring gear is supported the structure, in a more simple structure can be the synchronous rotational speed of the ring gear and the pinion. However, usually, in the miniaturization of the motor, than the gear number of the pinion gear and gear ring the degree to ten times, the pinion gear and the ring gear due to the size of the limitation to the structure but not in the same shaft.

Therefore, from the pinion gear toward the ring gear against the friction surface of the synchronizing mechanism always slide in the synchronization, it is difficult to realize the same is completely synchronous phase. Therefore, because the engagement is very difficult to reverse direction, therefore, the prohibition of the control on such measures need to be taken.

Furthermore, in the synchronization mechanism, the synchronization after the time point of contact with the ring gear and the pinion, in addition to a time point of the phase coincidence situation, the ring gear and the pinion will be generated between sliding, and with the same phase point. In this way, the structure of the synchronizing mechanism in use, sliding synchronous after the use, contact the pinion and the gear ring.

Therefore, at this moment there is the problem of abrasion of the noise and, in addition, the need for synchronization or as a result of the wearing surface of and the need for additional space such a problem, the structure of the pinion gear and ring gear of the large space, so it is very difficult to realize.

Therefore, as the pinion and the ring gear of a simple and the method of meshing, in addition, for example, in the case of using a synchronization mechanism, such as the Patent document 3 that, in order to make the pinion and the ring gear can be easily engaged, can be thought that the improved shape of the front end of the pinion gear, such as the chamfer is arranged the rainwater. Therefore, in Patent document 3 in, can be inserted into the corresponding to the chamfer the amount of the space formed by, and can obtain surface guiding effect is.

In this, according to the Patent literature 3, if it is under the state of the ring gear the engagement of the stop, the chamfer of the guiding effect. However, in the course of rotating the ring gear relative to the pinion gear under the condition of different rotational speed, will be the contact of the chamfered portion of the two gear collision, thus will produce the pinion gear in the axial direction of the force component of the driver. Therefore, in the course of rotating the ring gear, the chamfer angle becomes negative.

In this way, the ring gear is meshed with the pinion gear in the course of rotating under the condition of, if not the abutting the instantaneous more reliable synchronization and phase coincidence, it will produce the noise, caused by abrasion of reducing the service life of, in addition, will also produce due to the losses incurred engagement time of the starting is delayed, and the like.

In particular, when the pinion and the ring gear of the speed difference between the case of very large, if not pushed by synchronizing the time of mutual friction of the variable-length, then the noise sounds very large.

Content of the invention

The invention, in order to solve this kind of problem and for, the purpose is to obtain a kind of engine starting device, when in the process of rotating the ring gear with the pinion gear when the ring gear, even if the ring gear, the rotational speed of the pinion gear under the condition of very large difference, no matter whether the rotation is in, the pinion and the gear ring can be simply carried out by engagement re-starting.

The starting device of the engine of this invention, including: starting motor; pinion department, the pinion part of the output shaft of the starting motor with the side of the spline, and sliding along the axial direction, and has a one-way clutch, the one-way clutch to rotate in the same direction with respect to the rotation of the engine idling; pushing-out mechanism, the push-out mechanism to the part to move the pinion gear the position of the ring gear; the ring gear, the gear ring is pushed out of the mechanism through the introduction of pinion department of the pinion gear, to transmit the rotary force of the starting motor, so that the engine starting, the inertia of the engine after stopping of the engine in the course of rotating under the condition of re-start-up, can also be based on the prescribed conditions for re-starting, a pinion pinion department monomer to the axial movement, depending on tooth ring of the pinion with the end of one side of the non-torque transmitting surface on one side of the tooth while gearings is arranged between the curved shape of a chamfered section.

According to the invention, the engine starting apparatus, since the monomer along the axial direction to movement of the pinion, and depending on tooth ring of the pinion with the end of one side of the non-torque transmitting surface on one side is arranged between the tooth face of a curved surface shape with a chamfered portion of while gearings, therefore, when the can be obtained in the course of rotating the ring gear with the pinion gear when the ring gear, even if the ring gear, the rotational speed of the pinion gear under the condition of very large difference, no matter whether the rotation is in, the pinion and the gear ring can be simply carried out by engagement of the engine starting device for starting.

Description of drawings

Figure 1 is the exploded view of the embodiment of the invention 1 the engine-starting device.

Figure 2 is the cutaway view of the embodiment of the invention 1 the engine starting device is mounted on the engine.

Figure 3 is the decomposition three-dimensional view of the embodiment of the invention 1 the pinion department forming parts of the.

Figure 4 is the three-dimensional view of the embodiment of the invention said 1 of the shape of the pinion gear.

Figure 5 is the schematic view of the embodiment of the invention 1 in, the clockwise rotation of the ring gear under the condition of, the pinion push-out balance pistion the gear ring.

Figure 6 is the schematic view of the embodiment of the invention 1 in, the clockwise rotation of the ring gear under the condition of, push out the pinion gear when the gear ring, and fig. 5 different.

Figure 7 is the schematic view of the embodiment of the invention 1 in, and the ring gear under the condition of reverse rotation, the pinion push-out balance pistion the gear ring.

Figure 8 is the schematic view of the embodiment of the invention 1 in, and the ring gear under the condition of reverse rotation, push out the pinion gear with the ring gear during the engagement, and the chart 7 different.

Figure 9 is the diagram of the embodiment of the invention said 1 of the pinion and the ring gear of the relative position relationship.

Figure 10 is the diagram of the embodiment of the invention said 1 the pinion and the ring gear of the relationship of the relative position, and Figure 9 different.

Mode of execution

The following, the use of the Figure the starting device of the engine of this invention a description of the preferred embodiment.

Embodiment 1

Figure 1 is the exploded view of the embodiment of the invention 1 the engine-starting device. Figure 1 of the embodiment shown in 1 of driving influence department engine starting device by the electric motor 10, shaft 20, pinion department 30, attract coil portion 40, plunger 50, rod 60, bracket 70, limiting piece 80 and a speed reduction gear part 90 form.

Motor driving influence department 10 start an engine. Shaft 20 through a reduction gear portion 90 is combined with the output of the electric motor shaft. pinion department 30 and the shaft 20 of the helical spline the overrunning clutch (overrunning clutch: one-way clutch) integrated, can slide in the axial direction.

Attracting coil portion 40 through the switch is turned on to the plunger 50 to attract. Rod 60 is composed of a suction generated by the plunger 50 of the mobile transmitted to pinion department 30. Bracket 70 driving influence department by the motor 10, shaft 20 and pinion department 30 of the various parts a through pinion of the stop member 80 is fixed on the engine side.

Figure 2 is the cutaway view of the embodiment of the invention 1 the engine starting device is mounted on the engine. In the case of engine startup, when the switch is turned on, the relay contact is closed, current in attracting coil portion 40 of the suction coil 41 to flow in, thus the plunger 50 to attract. When the plunger 50 is attracted, rod 60 to be pulled and, rod 60 to a rod rotating shaft center 61 as the center to rotate.

Rotation of the pole 60 of the plunger 50 to the opposite end of side pinion department 30 out of, as a result, the small gear portion 30 along the shaft 20 of the spline of the pressed while rotating. Furthermore, because the plunger 50 from being sucked into the, so can the spring 45 will be compressed on one side of the core 42 into the. Therefore, can utilize the mobile contact portion 43 of the motor contact 44a, 44b closed, thereby to start the energization of the drive motor, in order to make the rotation of the motor.

Figure 3 is the decomposition three-dimensional view of the embodiment of the invention 1 the pinion department 30 forming parts of the. pinion department 30 including the overrunning clutch 31, core 32, the helical spring 33, pinion 34 and keep the parts 35.

Figure 4 is the three-dimensional view of the embodiment of the invention said 1 pinion 34 shape. As shown in Figure 4, the pinion 34 depending on tooth ring of 100 with the end of one side of the non-torque transmitting side by the surface 34c between, along with surface 34c of the curved surface shape of the tooth face is provided with a chamfered portion 34d, in addition, the pinion gear 34 of the outer diameter section, the outer diameter along the tooth is provided with a chamfered portion 34e.

In this, on the chamfered portion 34d in the axial direction and rotation direction of the size of the on, such as use chart 6, Figure 8 and in the rear, as described, in the axial direction to the corner (equivalent to Figure 6, Figure 8 of the up and down direction on the paper) is greater than or equal to the size of the chamfered portion in the rotation direction (equivalent to Figure 6, Figure 8 of the left and right direction of the paper surface) on the way of the magnitude of the (in other words, in order to increase the Figure 6 shown in the angle θ, and formed in the axial direction becomes deeper the shape of the chamfer) is provided curved shape. Furthermore, the pinion gear 34 which is arranged on the inner side of the spindle 32 engaged with the groove 34a.

A through as described above, when the ring gear 100 the inertial rotation of the engine after stopping of the engine exists in the process of re-start-up under the condition of, through the relay contact is closed, the attracting coil 41 is energized, the pinion can be 34 push-out and gear ring 100 abuts.

Figure 5 is the schematic view of the embodiment of the invention 1 in, the ring gear 100 the case of the clockwise rotation, the pinion gear 34 sliding with the ring gear 100 a balance pistion. More specifically, in the illustration the ring gear 100 when the meshing action is in the, ring gear 100 and a chamfered portion 34d of the contact.

In the Figure 5 when such contact, as the use of the ring gear 100 is transmitted to the rotation of the pinion gear 34 a transmission force of the, produce a the overrunning clutch 31 towards the idling direction of the force of the idling.

Therefore, the overrunning clutch 31 also play for the ring gear 100 rotates fast when the role of the synchronization. Furthermore, inverted corner 34d along the non-torque transmitting side by the surface 34c is formed of the curved surface of the tooth face. Therefore, in the axial direction when the vertical is observed on the cross section of, the ring gear 100 of the teeth and the pinion 34 tooth throughout meshed with the state of the same. That is to say, the rotating loss of the generated.

In the meshed tooth each other the state of the condition of the same not, the ring gear 100 and the pinion 34 different speed vector of their respective teeth. Therefore, said from the result, the contact position offset in the axial direction, not only unable to transmit a stable rotational force, there is the situation becomes the ball opens the strength, is in an unstable state.

In this, if the in order to obtain the above-mentioned stabilized and the rotation force of the rotating direction of the minimum required as the strength supposes Fr, the chamfered portion 34d of the angle of the chamfer angle is set to θ, generating a rotational force required in the axial direction component of the counterforce of the Fz satisfy the following relations:

Fz=Fr/tan θ (1)

Therefore, as long as the introduction of the pinion relative to the Fz Fp satisfy the following relationship between the force of the, can be the synchronous side of one side of the pinion gear 34 is pushed into the ring gear 100.

Fp>Fz (2)

Fp the pinion gear, the greater the force of the launch, the better meshing. However, if the pinion gear is excessive Fp introduction of force, the pinion gear 34 and the ring gear 100 and the load of collision is large, and the result of the increased wear and the like. Therefore, preferably the introduction of the force of the pinion gear do not exceed Fp necessary to limit the load of the most appropriate. Furthermore, in the embodiment 1 in the structure, the said Fp is composed of a spiral spring 33 according to the pressure exerted.

Therefore, in order to as far as possible, Fz reduces the strength, need to increase the angle θ. Figure 6 is the schematic view of the embodiment of the invention 1 in, the ring gear 100 the case of the clockwise rotation, the pinion gear 34, the push out 100 during the engagement, and Figure 5 different. More specifically, the angle θ is increased to more than the previous Figure 5 more of the situation.

In this, the angle θ in other words is equivalent to the increase of an inverted corner in the axial direction is equal to the size of the chamfered portion larger than in the rotation direction on the way of the magnitude of the (in other words, as shown in Figure 6, in order to set as in the axial direction becomes more deep the shape of the chamfer) is provided with a chamfered portion 34d.

As shown in Figure 6, by increasing the angle θ, the force Fz becomes small, as long as it is can be Fp the force Fz can be pressed into the spring reaction force of the spring. In other words, by increasing the angle θ, even if the ring gear 100 in the process of rotation, also can make the pinion 34 instantaneous synchronous with the ring gear 100 is engaged.

Figure 7 is the schematic view of the embodiment of the invention 1 in, the ring gear 100 and fluctuations under the condition of reverse rotation, the pinion gear 34 sliding with the ring gear 100 a balance pistion. As shown in Figure 7, the pinion gear 34 with the ring gear 100 by the rotation of a chamfered portion 34d into the (with reference to Figure 7 (a), fig. 7 (b)), the ring gear 100 and the torque transmission surface 34b engaged, in order to form the initial engagement (with reference to Figure 7 (c)).

Once the torque transmission surface 34b and the ring gear 100 to the pinion gear to be rotated in the reverse rotation, the small gear portion is a spiral gear 21 meshing, and has been engaged to the final. Furthermore, through the has been engaged to the finally, to ensure that the length of the torque transmitting surface (the length of the torque transmitting engagement) 36b (with reference to Figure 7 (d)).

At this moment, torque non-transmitting surface on one side of the surface 34c is assumed that the length of the contact 36c. In other words, the surface 34c is provided that is equivalent to in the chamfered portion 34d as the non-torque transmitting surface on the surface of one side of the surface of the and the remaining, in the rotation of the motor when starting the engine to the, surface 34c hits the tooth in the fluctuation of the surface of the collision when the (cranking), at the time of the collision, the torque of the non-transfer surface and one side surface 34c of the length in the axial direction (non-torque transmitting side collision length) to 36c.

In the above-mentioned action, the initial engagement length 36a is very important. If it is not possible to ensure that initial engagement length 36a, then to the ring gear 100 for cutting. Therefore, by increasing chamfered portion 34d the depth of the in the axial direction, the length can be the initial engagement 36a to ensure that a longer.

Figure 8 is the schematic view of the embodiment of the invention 1 in, the ring gear 100 and under the condition of reverse rotation, the pinion gear 34, the push out 100 during the engagement, and the chart 7 different. More specifically, the angle θ is increased to more than the previous Figure 7 more of the situation.

As shown in Figure 8, the pinion 34 when the initial collision with the ring gear 100 in contact with the end face of the (with reference to Figure 8 (a)), and along the chamfered portion 34d being drawn into a (with reference to Figure 8 (b)), with an initial engagement length 36a engaged (with reference to Figure 8 (c)). Since due to the angle θ and the axial depth becomes deeper, therefore, the length of the initial engagement to 36a to ensure that a longer.

Furthermore, and to ensure that initial engagement length 36a is equally important to the other point is individually mobile pinion gear. Because pinion department 30 to overrunning clutch 31, and the like of the combination of the moving parts, therefore, a very heavy weight.

Is opposite to this, in this embodiment is 1 pinion department of 30 in the structure, can be through pinion 34 monomer action, is only the mass moving the pinion 34 quality. Therefore, by increasing the acceleration, can be along a chamfered portion 34d are being engaged. Therefore, lighter weight of the pinion gear 34 as long as there is a can along the chamfered portion 34d is pushed into the surface of the strength can be pushed into. At is formed by the pushing force of spring 33 pressing load is applied.

Furthermore, the engagement of the torque transmission is carried out, as long as it can ensure that the length of the torque transmitting surface 36b can be, although non-torque transmitting surface on one side of the length 36c shortened, but as long as there is no extreme wear to the minimum level, there is no particular problem. In other words, chamfer part 34d to the pinion 34 and ring gear 100 is fully engaged under the state of (equivalent to Figure 8 (d)) of the non-torque transmitting the axial length of side 36c residual a minimum limit for the level of the way to form the surface of the non-torque transmitting side 34c.

In this way, as long as the design of the spiral spring 33, in order to exert the required positive transfers the side of the spring according to the pressure and in the reverse side and only along the chamfered portion 34d is pushed in the pushing of the spring load. With this design, when the gear ring 100 during the rotation process of the pinion 34 and ring gear 100 meshes with the, even when the ring gear 100, the pinion 34 the speed difference between the case of very large, to can be simply re-starting.

Increase in a chamfered portion 34d of the case of the chamfer angle θ, not only increases the size of the upward, also increase the circumferential direction (rotation direction) of an ideal size. However, at this time, if the excessive increase in the size of the circumferential direction, will no longer have the strength tooth itself. In this case, in order to also can pass along the surface of the non-torque transmitting side 34c is formed into the shape of the curved surface of the tooth face a chamfered portion 34d, as far as possible, to retain the pinion gear 34 of the tooth of the state of the thickness of the wall of a chamfer.

Furthermore, Figure 9 is the diagram of the embodiment of the invention said 1 of the pinion 34 and the ring gear 100 the relative position relationship. As shown in Figure 9, at the time of meshing, from the ring gear 100 and the pinion 34, the positional relationship of the overlapping point is an overlapping part 37a, 37b, 37c. Wherein the parts are in an overlapping part 37b.

However, in the embodiment 1 in the structure, cause the pinion 34 of the precision of the shaft or the pinion 34 of the work precision of the inclined, sometimes in an overlapping part 37c contact. In this case, the ring gear 100 and the shape of the pinion gear 34 against the edge part of the tooth crest interference, in the state of the can not rotate.

Therefore, in order to avoid this kind of state, such as the previous Figure 4 illustrated, effective is in the pinion gear 34 of the outer diameter section is provided with a chamfered portion 34e. Figure 10 is the diagram of the embodiment of the invention said 1 of the pinion 34 and the ring gear 100 of the relationship of the relative position, and Figure 9 different. As shown in Figure 10, the crest diameter section is provided with a chamfered portion 34e, in an overlap portion 37b and an overlapping part 37a the pinion 34 and ring gear 100 contact.

Through adopting this kind of structure, can make the ring gear 100 and the pinion 34 instantly engaged, to make the motor start-up. Furthermore, because the pinion gear 34 of the curved surface of the form by forging and, therefore, also can realize low cost.

As mentioned above, according to the embodiment 1, can be shaped into the with the structure of the movement along the axial direction. Furthermore, depending on tooth ring of the pinion with the end of one side of the non-torque transmitting surface on one side of between the tooth face of the, while gearings provided with a curved shape of a chamfered section. Because of having this kind of structure, therefore, the rotation of the ring gear can be realized in the course of the ring gear and the pinion gear, even if the ring gear, the rotational speed of the pinion gear under the condition of very large difference, no matter whether the rotation is in, the pinion and the gear ring can be simply carried out by engagement of the engine starting device for starting.

Furthermore, along the axial direction have the shape of the chamfered portion, thereby can be further reduced to the pressure of moving the pinion gear, and to ensure that initial engagement length is longer, thus can further improve the meshing performance.