JP4957104B2 - Starting device - Google Patents

Description

  The present invention relates to a starter, and more particularly to a starter that drives a load by allowing torque transmission from a prime mover to the load.

  For example, a friction clutch is used as a starting device for driving a load such as starting a vehicle (for example, Patent Document 1 below). When driving a stopped load by transmitting the power of a prime mover such as an engine to the load by engaging the friction clutch (starting the vehicle), it is necessary to temporarily slide the friction clutch so that the engine does not stall. Occurs. As the friction clutch slips, the friction clutch generates heat.

  In Patent Document 1, when there is a rotational speed difference between the driving side (input side) and the driven side (output side) of the friction clutch (wet multi-plate clutch), that is, the friction clutch slips. Sometimes, oil is supplied to the wet multi-plate clutch by driving the oil pump using this rotational speed difference. Thus, the wet multi-plate clutch that generates heat is cooled. On the other hand, when there is no difference in rotational speed between the driving side and the driven side of the wet multi-plate clutch, the driving of the oil pump is stopped.

  In addition, a continuously variable transmission according to Patent Document 2 below is disclosed.

Japanese Patent Publication No. 6-17691 JP-A-4-88241

  In Patent Document 1, since power transmission from the prime mover to the load is performed only through the clutch, it is necessary to set the torque capacity of the clutch to the maximum transmission torque from the prime mover to the load. As a result, the torque capacity of the clutch is increased.

  An object of this invention is to provide the starting apparatus which can reduce the torque capacity of a clutch.

  The starting device according to the present invention employs the following means in order to achieve the above-described object.

A starting device according to the present invention is a starting device that drives a load by allowing torque transmission from the prime mover to the load, and transmits the torque from the prime mover to the first rotational member. A second rotating member and a third rotating member to which the generated torque is distributed, a torque distributing mechanism for transmitting the torque distributed to the third rotating member to a load, and a first connected to the second rotating member A fastening member and a second fastening member coupled to the third rotating member, and distributed from the prime mover to the second rotating member and the third rotating member by adjusting a fastening force between the first fastening member and the second fastening member. And a clutch capable of adjusting the torque, the torque transmitted from the prime mover to the load is adjusted by adjusting the fastening force between the first fastening member and the second fastening member, and further from the prime mover. The torque transmitted to the load is the first SUMMARY rolling torque from member is distributed to the second rotary member is transmitted to the load through the clutch, to be distributed to the torque transmitted from the first rotary member to the third is distributed to the rotating member load And

  In one aspect of the present invention, a driven machine connected to the second rotating member, the driven machine capable of adjusting the torque distributed from the prime mover to the second rotating member and the third rotating member by adjusting the torque. It is preferable that the torque transmitted from the prime mover to the load is adjusted by adjusting the torque of the driven machine.

The starting device according to the present invention is a starting device that drives a load by allowing torque transmission from the prime mover to the load, and includes a first rotating member to which torque from the prime mover is transmitted, and a first rotating member A second rotating member and a third rotating member that distribute the torque transmitted to the first rotating member, the torque distributing mechanism transmitting the torque distributed to the third rotating member to the load, and the first rotating member. Including a first fastening member and a second fastening member coupled to the third rotating member, and adjusting the torque transmitted from the prime mover to the load by adjusting the fastening force between the first fastening member and the second fastening member. A clutch capable of adjusting the torque distributed from the prime mover to the second rotating member and the third rotating member by adjusting the torque, and a driven clutch coupled to the second rotating member. A first fastening member and a second fastening portion By torque in the fastening force and the driven machine are adjusted with the torque is adjusted torque transmitted from the prime mover to the load, further, the torque transmitted from the prime mover to the load, which is transmitted to the load through the clutch And the torque that is distributed from the first rotating member to the third rotating member and transmitted to the load .

  In one aspect of the present invention, when the rotation speed of the first rotation member is higher than the rotation speed of the third rotation member, the torque distribution mechanism has a rotation speed difference corresponding to the rotation speed difference between the second rotation member and the second rotation member. The differential mechanism is preferably a differential mechanism whose rotational speed is higher than the rotational speed of the first rotating member.

  In one aspect of the present invention, when increasing the torque transmitted from the prime mover to the load, priority is given to increasing the torque of the driven machine over increasing the fastening force between the first fastening member and the second fastening member. It is preferable to carry out. In this aspect, when the torque transmitted from the prime mover to the load is increased and the required torque of the load is equal to or less than the set value, the torque of the driven machine is increased without fastening the first fastening member and the second fastening member. Is preferable. Further, in this aspect, when the torque transmitted from the prime mover to the load is increased and the required torque of the load is larger than the set value, the first fastening member and the second fastening member are engaged with the driven machine generating torque. It is preferable to increase the fastening force with the member.

  In one aspect of the present invention, the driven machine is a hydraulic pump that sucks and discharges oil, and preferably includes adjusting means for adjusting the torque of the hydraulic pump by adjusting the discharge pressure of the oil from the hydraulic pump. It is. In this aspect, it is preferable that the oil discharged from the hydraulic pump is supplied to the clutch.

  In one aspect of the present invention, the torque distribution mechanism is a single pinion planetary gear mechanism including a sun gear, a carrier, and a ring gear, the first rotating member is a carrier, and the second rotating member is one of the sun gear and the ring gear. The third rotating member is preferably the other of the sun gear and the ring gear. In one aspect of the present invention, the torque distribution mechanism is a double pinion planetary gear mechanism including a sun gear, a carrier, and a ring gear, the first rotating member is a ring gear, and the second rotating member is a sun gear and a carrier. The third rotating member is preferably the other of the sun gear and the carrier.

  According to the present invention, the torque of the prime mover can be distributed to the torque transmitted via the clutch and the torque transmitted via the third rotating member of the torque distribution mechanism and transmitted to the load. Torque transmitted through the clutch can be reduced. As a result, the torque capacity of the clutch can be reduced and the clutch can be reduced in size.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings.

“Embodiment 1”
FIG. 1 is a diagram showing a schematic configuration of a power output apparatus including a starter 10 according to Embodiment 1 of the present invention. The starting device 10 according to the present embodiment drives the load 16 by allowing torque transmission from an engine (internal combustion engine) 12 as a prime mover to the load 16. When torque transmission from the engine 12 to the load 16 is permitted by the starting device 10, the power generated by the engine 12 is shifted by the transmission 14 and then transmitted to the load 16, for example, driving of the vehicle For example, it is used for driving the load 16.

  The starting device 10 is provided between the engine 12 and the transmission 14, and includes a planetary gear mechanism 18 including a sun gear S, a carrier C, and a ring gear R as rotating members, and the degree of freedom of rotation of the planetary gear mechanism 18. And a friction clutch 20 for limiting from 2 degrees of freedom to 1 degree of freedom. FIG. 1 shows an example in which the planetary gear mechanism 18 is a single pinion type planetary gear mechanism. The sun gear S is connected to the transmission 14 (load 16), and the carrier C is connected to the engine 12. The friction clutch 20 is constituted by, for example, a wet multi-plate clutch, and includes a plurality of driving side friction plates 26 (first fastening members) connected to the ring gear R and a plurality of driven side friction plates 28 (connected to the sun gear S). Second fastening member). When the drive side friction plate 26 and the driven side friction plate 28 of the friction clutch 20 are not fastened (not in contact), the friction clutch 20 is released. On the other hand, when the driving side friction plate 26 and the driven side friction plate 28 are fastened, the friction clutch 20 is engaged. The friction clutch 20 can be switched between engagement and disengagement using, for example, the hydraulic pressure of the hydraulic actuator or the electromagnetic force of the electromagnetic actuator. By controlling the electromagnetic force of the electromagnetic actuator, the fastening force (pressing force) of the friction clutch 20 (the driving side friction plate 26 and the driven side friction plate 28) can also be controlled. The friction clutch 20 is supplied with oil discharged from a hydraulic pump (not shown) for cooling and lubrication.

  Next, the operation of the starting apparatus 10 according to the present embodiment, in particular, the operation for interrupting power from the engine 12 to the load 16 will be described.

  When the fastening force between the driving side friction plate 26 and the driven side friction plate 28 is 0, that is, when the friction clutch 20 is in the released state, the coupling of the ring gear R and the sun gear S via the friction clutch 20 is released. Thus, the rotational freedom degree of the planetary gear mechanism 18 is maintained at two degrees of freedom. As a result, torque transmission from the engine 12 to the transmission 14 (load 16) is interrupted.

  Further, in the planetary gear mechanism 18, the rotational speeds of the three rotating members of the sun gear S, the carrier C, and the ring gear R are in the collinear relationship shown in the collinear diagram of FIG. 2, and therefore the rotational speed of the engine 12 (carrier C). Is Neng and the rotation speed of the sun gear S (driven friction plate 28) is Nout, the rotation speed Nr of the ring gear R (drive friction plate 26) is expressed by the following equation (1). However, in the formula (1), ρ is a gear ratio between the sun gear S and the ring gear R (a constant satisfying 0 <ρ <1).

  Nr = (1 + ρ) × Neng−ρ × Nout (1)

  From the equation (1), in a state where the engine 12 is driven to rotate and the rotation of the load 16 (sun gear S) is stopped, between the driving side friction plate 26 and the driven side friction plate 28 (ring gear R and A difference in rotational speed of (1 + ρ) × Neng occurs with the sun gear S).

  On the other hand, when the stopped load 16 is driven, for example, when the stopped vehicle is started, the fastening force between the driving side friction plate 26 and the driven side friction plate 28 while the engine 12 is generating power. Is gradually increased from 0 to engage the friction clutch 20. By applying a fastening force (pressing force) to the friction clutch 20, the torque of the engine 12 can be transmitted to the transmission 14 via the sun gear S while receiving the torque of the engine 12, and the torque of the engine 12 can be transmitted to the friction clutch 20. 20 can be transmitted to the transmission 14. As a result, torque transmission from the engine 12 to the transmission 14 (load 16) is allowed, and the load 16 can be driven, such as starting the vehicle.

  In the alignment chart of FIG. 2, the carrier C connected to the engine 12 is arranged between the sun gear S connected to the transmission 14 (load 16) and the ring gear R connected to the drive side friction plate 26. Therefore, the torque transmitted from the engine 12 to the carrier C is distributed to the sun gear S and the ring gear R in a state where the torque ratio is a predetermined ratio ρ. The torque distributed to the sun gear S is transmitted to the transmission 14 (load 16), and the torque distributed to the ring gear R is transmitted to the transmission 14 (load 16) via the friction clutch 20. Thus, the planetary gear mechanism 18 functions as a torque distribution mechanism that distributes the torque from the engine 12 transmitted to the carrier C to the sun gear S and the ring gear R.

  As shown in the nomogram of FIG. 2, if the transmission torque of the friction clutch 20 (torque acting on the ring gear R) is Tfric, the torque acting on the sun gear S is ρ × Tfric. The torque transmitted to 14 is (1 + ρ) × Tfric. Since the value of Tfric (transmission torque of the friction clutch 20) changes according to the fastening force (pressing force) of the friction clutch 20 (the driving side friction plate 26 and the driven side friction plate 28), the fastening force of the friction clutch 20 is adjusted. Thus, the torque ρ × Tfric and Tfric distributed from the engine 12 to the sun gear S and the ring gear R can be adjusted, and the torque (1 + ρ) × Tfric transmitted from the engine 12 to the transmission 14 (load 16). Can be adjusted.

  Further, as shown in the collinear diagram of FIG. 2, when the rotational speed Neng of the engine 12 (carrier C) is higher than the rotational speed Nout of the sun gear S, the rotation according to the rotational speed difference (Neng−Nout). The rotational speed Nr of the ring gear R is higher than the rotational speed Neng of the carrier C by the speed difference ρ × (Neng−Nout). At this time, a rotational speed difference of (1 + ρ) × (Neng−Nout) is generated between the driving side friction plate 26 and the driven side friction plate 28, and the friction clutch 20 slips. As described above, the planetary gear mechanism 18 generates a rotational speed difference ρ × (Neng−Nout) between the ring gear R and the carrier C according to the rotational speed difference (Neng−Nout) between the carrier C and the sun gear S. It also functions as a differential mechanism.

  As the rotational speed Nout with the sun gear S increases and the rotational speed difference (Neng−Nout) between the carrier C and the sun gear S decreases, the rotational speed difference ρ × (Neng− Nout) also decreases. When the rotational speed Nout of the sun gear S becomes equal to the rotational speed Neng of the carrier C, the rotational speed Nr of the ring gear R becomes equal to the rotational speed Nout of the sun gear S and the rotational speed Neng of the carrier C, and the drive side friction plate 26 and the driven side The rotational speed difference from the friction plate 28 is eliminated (the friction clutch 20 does not slip). In the engaged state of the friction clutch 20, the ring gear R and the sun gear S are coupled via the friction clutch 20 to limit the rotational freedom of the planetary gear mechanism 18 to one degree of freedom, whereby the planetary gear mechanism 18. Is in a directly connected state in which the sun gear S, the carrier C, and the ring gear R rotate together.

  As shown in FIG. 3, when power is transmitted from the engine 12 to the load 16 (when the friction clutch 20 is engaged), the power transmitted from the engine 12 to the carrier C of the planetary gear mechanism 18 is the sun gear S and the ring gear. Distributed to R. The power distributed to the sun gear S and the power distributed to the ring gear R and transmitted via the friction clutch 20 are combined at the input side of the transmission 14, and the combined power is shifted by the transmission 14. Then, it is transmitted to the load 16.

  In general, a starter has a function of transmitting / cutting power between an engine and a load, and a function of transmitting power so that the engine does not stall when driving a load in a stopped state (when the vehicle starts). Is required. In a starting device using a friction clutch, it is necessary to temporarily slide the friction clutch in order to transmit power so that the engine does not stall. The slip of the friction clutch causes a loss in power transmission through the friction clutch, and the friction clutch generates heat. In the configuration in which power is transmitted between the engine and the load via only the friction clutch as in Patent Document 1, it is necessary to set the torque capacity of the friction clutch to the maximum transmission torque from the engine to the load. As a result, the torque transmission capacity of the friction clutch is increased and the size of the apparatus is increased.

  On the other hand, in the present embodiment, the torque of the engine 12 is divided into torque transmitted through the friction clutch 20 (friction clutch transmission force) and torque transmitted through the sun gear S (gear direct force). Then, it can be transmitted to the load 16. Accordingly, the torque transmitted (shared) by the friction clutch 20 at the time of torque transmission from the engine 12 to the load 16 can be reduced. Therefore, the torque transmission capacity of the friction clutch 20 can be reduced, and the area of the friction plates 26 and 28 and the amount of oil supplied to the friction plates 26 and 28 for cooling and lubrication can be reduced. As a result, the starting device 10 can be reduced in size.

  In the above description of the first embodiment, the drive side friction plate 26 of the friction clutch 20 is connected to the ring gear R of the planetary gear mechanism (single pinion type planetary gear mechanism) 18, and the driven side friction of the transmission 14 and the friction clutch 20. The plate 28 is connected to the sun gear S of the planetary gear mechanism 18. However, in the present embodiment, the driving side friction plate 26 can be connected to the sun gear S, and the transmission 14 (load 16) and the driven side friction plate 28 can be connected to the ring gear R. In this case, torque distributed from the engine 12 to the ring gear R is transmitted to the transmission 14, and torque distributed from the engine 12 to the sun gear S is transmitted to the transmission 14 via the friction clutch 20. In this case as well, the torque of the engine 12 can be distributed to the friction clutch transmission force via the friction clutch 20 and the gear direct force via the ring gear R and transmitted to the load 16, and the fastening force of the friction clutch 20 can be transmitted. The torque transmitted from the engine 12 to the load 16 can be adjusted.

  In the present embodiment, the planetary gear mechanism 18 can also be configured by a double pinion type planetary gear mechanism. In this case, the engine 12 is connected to the ring gear R, the driving side friction plate 26 is connected to the carrier C, and the transmission 14 (load 16) and the driven side friction plate 28 are connected to the sun gear S. As a result, the torque transmitted from the engine 12 to the ring gear R is distributed to the sun gear S and the carrier C in a state where the torque ratio is a predetermined ratio ρ / (1-ρ), and the torque distributed to the sun gear S is While being transmitted to the transmission 14, the torque distributed to the carrier C is transmitted to the transmission 14 via the friction clutch 20. Alternatively, the engine 12 may be connected to the ring gear R, the driving side friction plate 26 may be connected to the sun gear S, and the transmission 14 (load 16) and the driven side friction plate 28 may be connected to the carrier C. As a result, torque distributed from the engine 12 to the carrier C is transmitted to the transmission 14, and torque distributed from the engine 12 to the sun gear S is transmitted to the transmission 14 via the friction clutch 20. Also in these cases, the torque of the engine 12 can be distributed to the friction clutch transmission force and the gear direct force and transmitted to the load 16, and by adjusting the fastening force of the friction clutch 20, the load from the engine 12 to the load 16 can be adjusted. The torque transmitted to can be adjusted.

“Embodiment 2”
FIG. 4 is a diagram showing a schematic configuration of a power output device including the starting device 10 according to the second embodiment of the present invention. In the following description of the second embodiment, the same or corresponding components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

  In the present embodiment, compared to the first embodiment, a continuously variable transmission (CVT) is used as the transmission 14, and the front and rear are located between the engine 12 and the starting device 10 (the carrier C of the planetary gear mechanism 18). A forward / reverse switching mechanism 34 is provided. The forward / reverse switching mechanism 34 here has a clutch and a brake, and either one of the clutch and the brake is selectively engaged. The forward / reverse switching mechanism 34 transmits the torque from the engine 12 to the starting device 10 (carrier C) without reversing the direction when the clutch is engaged, and transmits the torque from the engine 12 in the direction when the brake is engaged. Reversed and transmitted to carrier C. However, in the present embodiment, the forward / reverse switching mechanism 34 may be omitted and a stepped transmission (AT) may be used as the transmission 14.

  Further, in the present embodiment, a hydraulic pump 32 as a driven machine is connected to the ring gear R of the planetary gear mechanism 18. The hydraulic pump 32 sucks oil stored in a reservoir (not shown), gives energy to the oil, and discharges it. The oil discharged from the hydraulic pump 32 is supplied to the contact portion between the drive side friction plate 26 and the driven side friction plate 28 for cooling and lubrication of the friction clutch 20. In addition, the oil discharged from the hydraulic pump 32 is also supplied to the lubrication part of the transmission 14, the clutch and brake of the forward / reverse switching mechanism 34, and the like. Furthermore, a pressure regulating valve 36 that adjusts the pressure of oil discharged from the hydraulic pump 32 is provided on the discharge side of the hydraulic pump 32. The drive control of the pressure regulating valve 36 is performed by the electronic control unit 42, and the torque of the hydraulic pump 32 can be controlled by controlling the pressure of oil discharged from the hydraulic pump 32 by the drive control of the pressure regulating valve 36.

  In the present embodiment, when the friction clutch 20 is in the released state and the torque of the hydraulic pump 32 is adjusted to 0 by the pressure regulating valve 36, torque transmission from the engine 12 to the transmission 14 (load 16) is cut off. Has been. In a state where the engine 12 is rotationally driven and the rotation of the load 16 (sun gear S) is stopped, the hydraulic pump 32 idles without performing work to give energy to the oil.

  On the other hand, as in the first embodiment, the fastening force (pressing force) between the driving side friction plate 26 and the driven side friction plate 28 is gradually increased from 0 (the friction clutch 20 is engaged), whereby the engine 12 The torque can be transmitted to the transmission 14 via the sun gear S while receiving the torque by the friction clutch 20, and the torque of the engine 12 can be transmitted to the transmission 14 via the friction clutch 20. As a result, torque transmission from the engine 12 to the transmission 14 (load 16) can be allowed, and the load 16 can be driven, such as starting the vehicle.

  Further, in the present embodiment, the torque of the hydraulic pump 32 is gradually increased from 0 by the drive control of the pressure regulating valve 36, so that the torque of the engine 12 is received by the hydraulic pump 32 and transmitted to the transmission 14 via the sun gear S. can do. This also allows torque transmission from the engine 12 to the transmission 14 (load 16).

  The torque transmitted from the engine 12 to the carrier C is distributed to the sun gear S and the ring gear R in a state where the torque ratio is a predetermined ratio ρ, as in the first embodiment. Assuming that the transmission torque of the friction clutch 20 is Tfric and the torque of the hydraulic pump 32 is Tpump, the torque acting on the ring gear R is (Tfric + Tpump) as shown in the collinear diagram of FIG. ρ × (Tfric + Tpump). Therefore, the torque transmitted from the engine 12 to the transmission 14 is (1 + ρ) × Tfric + ρ × Tpump. Therefore, also in this embodiment, the torque ρ × (Tfric + Tpump) and (Tfric + Tpump) distributed from the engine 12 to the sun gear S and the ring gear R are adjusted by adjusting the fastening force (pressing force) of the friction clutch 20. The torque (1 + ρ) × Tfric + ρ × Tpump transmitted from the engine 12 to the transmission 14 (load 16) can be adjusted. Furthermore, in this embodiment, the torque ρ × (Tfric + Tpump) and (Tfric + Tpump) distributed from the engine 12 to the sun gear S and the ring gear R can be adjusted also by adjusting the torque Tpump of the hydraulic pump 32. Torque (1 + ρ) × Tfric + ρ × Tpump transmitted from the engine 12 to the transmission 14 (load 16) can be adjusted.

  Also in the present embodiment, when the friction clutch 20 slips, that is, when the rotational speed Neng of the engine 12 (carrier C) is higher than the rotational speed Nout of the sun gear S as shown in the collinear diagram of FIG. The planetary gear mechanism 18 has the rotational speed Nr of the ring gear R higher than the rotational speed Neng of the carrier C by the rotational speed difference ρ × (Neng−Nout) corresponding to the rotational speed difference (Neng−Nout). Functions as a differential mechanism. On the other hand, when the friction clutch 20 is not slipped, the planetary gear mechanism 18 is in a directly connected state in which the sun gear S, the carrier C, and the ring gear R rotate together. Therefore, when the friction clutch 20 slips, the rotational speed Npump of the hydraulic pump 32 connected to the ring gear R can be increased as compared to when the friction clutch 20 does not slip. The oil flow rate discharged from the pump 32 can be increased. The rotational speed Npump of the hydraulic pump 32 is equal to the rotational speed Nr of the ring gear R and is expressed by the above-described equation (1). Therefore, the relationship of the rotational speed Npump of the hydraulic pump 32 to the speed ratio e (= Nout / Neng) between the rotational speed Nout of the sun gear S and the rotational speed Neng of the engine 12 (carrier C) is as shown in FIG.

  Also in the present embodiment described above, the torque of the engine 12 is distributed to the friction clutch transmission force transmitted via the friction clutch 20 and the gear direct force transmitted via the sun gear S, and transmitted to the load 16. be able to. Furthermore, in the present embodiment, when torque is transmitted from the engine 12 to the load 16, the torque of the engine 12 can be received by both the hydraulic pump 32 and the friction clutch 20. It can be further reduced. Therefore, the torque transmission capacity of the friction clutch 20 can be further reduced, and the friction clutch 20 can be downsized.

  As shown in FIG. 7, the torque of the engine 12 connected to the carrier C of the planetary gear mechanism 18 is received by the hydraulic pump 32 connected to the ring gear R of the planetary gear mechanism 18 to the load 16 from the engine 12. In the configuration in which the torque transmission is allowed, the torque transmitted from the engine 12 to the load 16 increases with an increase in the torque of the hydraulic pump 32. Therefore, it is necessary to increase the maximum torque of the hydraulic pump 32 as the maximum torque of the engine 12 increases, leading to an increase in the size of the hydraulic pump 32.

  In contrast, in the present embodiment, when torque is transmitted from the engine 12 to the load 16, the torque of the engine 12 can be received by both the hydraulic pump 32 and the friction clutch 20, so that the hydraulic pump 32 receives (shares). Torque can be reduced. Accordingly, the maximum torque of the hydraulic pump 32 can be reduced, and the hydraulic pump 32 can be downsized.

  Further, as described above, in the starting device using the friction clutch, it is necessary to temporarily slide the friction clutch so that the engine does not stall. When slippage occurs in the friction clutch, it is desirable to supply a large amount of oil to the friction clutch by a hydraulic pump in order to cool and lubricate the heat generating friction clutch. On the other hand, when the friction clutch is not slipped, no frictional heat is generated in the friction clutch, so that it is not necessary to supply a large amount of oil to the friction clutch. In Patent Document 1, when there is a rotational speed difference between the input side and the output side of the friction clutch (when the friction clutch slips), the hydraulic pump is operated using this rotational speed difference. By driving, oil for cooling and lubrication is supplied to the friction clutch. However, in Patent Document 1, when there is no rotational speed difference between the input side and the output side of the friction clutch (when the friction clutch is not slipped), the drive of the hydraulic pump is stopped. For this reason, unless another hydraulic pump is provided, oil cannot be supplied to other lubrication units or the like.

  On the other hand, in the present embodiment, when the friction clutch 20 slips, the rotational speed difference ρ × (Neng−Nout) corresponding to the rotational speed difference (Neng−Nout) between the engine 12 and the sun gear S. The rotational speed Npump of the hydraulic pump 32 becomes higher than the rotational speed Neng of the engine 12. As a result, when the friction clutch 20 is slipping, the flow rate of the oil discharged from the hydraulic pump 32 can be increased by an amount corresponding to the rotational speed difference (Neng−Nout). A sufficient amount of oil for lubrication can be supplied to the friction clutch 20. Further, the rotational speed Npump (oil discharge) of the hydraulic pump 32 increases as the sliding speed of the friction clutch 20 (the rotational speed difference between the driving side friction plate 26 and the driven side friction plate 28) (1 + ρ) × (Neng−Nout) increases. Flow rate) can be increased, so that the oil supply flow rate to the friction clutch 20 can also be increased. On the other hand, when the friction clutch 20 is not slipped, the rotational speed Npump of the hydraulic pump 32 becomes equal to the rotational speed Neng of the engine 12 (and the rotational speed Nout of the sun gear S). As a result, oil having a flow rate corresponding to the rotational speed Neng of the engine 12 can be discharged from the hydraulic pump 32, so that the oil discharged by the hydraulic pump 32 can be discharged from the transmission 14 without providing another hydraulic pump. It can be supplied to the lubrication section, the clutch and brake of the forward / reverse switching mechanism 34, and the like. Thus, according to the present embodiment, the oil discharge flow rate is increased by increasing the rotational speed Npump of the hydraulic pump 32 when the friction clutch 20 slips (heat generation) without increasing the discharge capacity of the hydraulic pump 32. Thus, a sufficient flow rate of oil for cooling and lubrication can be efficiently supplied to the friction clutch 20.

  Next, in this embodiment, a preferred specific example in the case where the load 16 is driven (the vehicle is started) by controlling the fastening force of the friction clutch 20 and the torque of the hydraulic pump 32 by the electronic control unit 42 will be described. .

  When the required torque TL of the load 16 is small, the pressing force is not applied to the friction clutch 20 (Tfric = 0), and the torque Tpump is generated in the hydraulic pump 32 by the drive control of the pressure regulating valve 36, so that the load 16 The transmitted torque ρ × γ × Tpump (γ is the transmission ratio of the transmission 14) can be made the required torque TL. Therefore, when the torque transmitted from the engine 12 to the load 16 is increased and the required torque TL of the load 16 is equal to or less than the set value T0, the electronic control unit 42 does not engage the friction clutch 20 (drive side). The torque Tpump of the hydraulic pump 32 is increased by drive control of the pressure regulating valve 36 (without fastening the friction plate 26 and the driven side friction plate 28). At this time, the torque of the engine 12 is received by the hydraulic pump 32 without being received by the friction clutch 20. Note that the set value T0 here is set based on the maximum torque that the hydraulic pump 32 can generate.

  On the other hand, when the required torque TL of the load 16 is large, the torque transmitted to the load 16 cannot be made the required torque TL only by receiving the torque of the engine 12 only by the hydraulic pump 32. Therefore, when the torque transmitted from the engine 12 to the load 16 is increased and the required torque TL of the load 16 is larger than the set value T0, the electronic control device 42 controls the hydraulic pump 32 by driving control of the pressure regulating valve 36. In a state where the torque Tpump is generated, the transmission torque Tfric of the friction clutch 20 (fastening force between the driving side friction plate 26 and the driven side friction plate 28) is increased. As a result, the torque of the engine 12 can be received by both the hydraulic pump 32 and the friction clutch 20, and the torque ((1 + ρ) × Tfric + ρ × Tpump) × γ transmitted to the load 16 can be made the required torque TL. . The required torque TL of the load 16 can be set based on, for example, the accelerator opening (detected by a sensor not shown).

  According to the control described above, when the torque transmitted from the engine 12 to the load 16 is increased, the transmission torque Tfric of the friction clutch 20 (fastening force between the driving side friction plate 26 and the driven side friction plate 28) is increased. Since the priority is given to increasing the torque Tpump of the hydraulic pump 32 rather than causing it to occur, the frequency with which the friction clutch 20 slips can be reduced. Therefore, the heat generation of the friction clutch 20 can be further suppressed, and the durability of the friction clutch 20 can be improved.

  In the present embodiment, when the friction clutch 20 is not overheated, torque is transmitted from the engine 12 to the load 16 by applying a pressing force to the friction clutch 20 without generating torque in the hydraulic pump 32. Can be done. Therefore, when the torque transmitted from the engine 12 to the load 16 is increased and the temperature τ (detected by a sensor not shown) of the friction clutch 20 is equal to or lower than a predetermined value τ0, the electronic control unit 42 applies torque to the hydraulic pump 32. Without generating the transmission torque Tfric (fastening force between the driving side friction plate 26 and the driven side friction plate 28) of the friction clutch 20 can be increased. At this time, the torque of the engine 12 is received by the friction clutch 20 without being received by the hydraulic pump 32. On the other hand, when the torque transmitted from the engine 12 to the load 16 is increased and the temperature τ of the friction clutch 20 is higher than the predetermined value τ0, the electronic control unit 42 increases the torque Tpump of the hydraulic pump 32. As a result, a sufficient amount of oil can be supplied from the hydraulic pump 32 to the friction clutch 20, and the friction clutch 20 can be cooled. According to the above control, power transmission from the engine 12 to the load 16 can be efficiently performed while preventing the friction clutch 20 from being overheated.

  Further, as described above, when the friction clutch 20 is slipping, the oil flow rate discharged from the hydraulic pump 32 can be increased. Therefore, the oil flow rate necessary for cooling the friction clutch 20 is increased. It can be secured sufficiently. Therefore, when the electronic control unit 42 drives the stopped load 16 (starts the vehicle) by increasing the torque transmitted from the engine 12 to the load 16, the torque Tpump of the hydraulic pump 32 and the friction clutch 20. The transmission torque Tfric (the fastening force between the driving side friction plate 26 and the driven side friction plate 28) can also be increased. Also by this, oil at a flow rate sufficient for cooling from the hydraulic pump 32 to the friction clutch 20 can be supplied, so that power transmission from the engine 12 to the load 16 can be performed while preventing the friction clutch 20 from overheating. It can be done efficiently.

  In this embodiment, a generator can be connected to the ring gear R of the planetary gear mechanism 18 as a driven machine. In this case, the electronic control unit 42 can control the torque of the generator by controlling the current of the generator. Also in this case, when the torque is transmitted from the engine 12 to the load 16, the torque of the engine 12 can be received by both the friction clutch 20 and the generator, so that the torque shared by the friction clutch 20 and the generator can be reduced. Further, the friction clutch 20 and the generator can be reduced in size. When the friction clutch 20 slips, the generator rotational speed Ngen is equal to the rotational speed difference ρ × (Neng−Nout) corresponding to the rotational speed difference (Neng−Nout) between the engine 12 and the sun gear S. (= Nr) becomes higher than the rotational speed Neng of the engine 12, and the power generation amount (generated power) by the generator can be increased.

  In this embodiment, the hydraulic pump 32 (or generator) and the drive side friction plate 26 of the friction clutch 20 are connected to the sun gear S of the planetary gear mechanism (single pinion type planetary gear mechanism) 18, and the transmission 14 and the friction are connected. The driven friction plate 28 of the clutch 20 can be connected to the ring gear R of the planetary gear mechanism 18. In this case as well, the torque of the engine 12 can be distributed to the friction clutch transmission force via the friction clutch 20 and the gear direct force via the ring gear R and transmitted to the load 16, and the fastening force of the friction clutch 20 can be transmitted. The torque transmitted from the engine 12 to the load 16 can be adjusted by adjusting the torque of the hydraulic pump 32 (or the generator).

  Also in the present embodiment, the planetary gear mechanism 18 can also be configured by a double pinion type planetary gear mechanism. In this case, the engine 12 is connected to the ring gear R, the hydraulic pump 32 (or generator) and the driving side friction plate 26 are connected to the carrier C, and the transmission 14 and the driven side friction plate 28 are connected to the sun gear S. . Alternatively, the engine 12 may be connected to the ring gear R, the hydraulic pump 32 (or generator) and the driving side friction plate 26 may be connected to the sun gear S, and the transmission 14 and the driven side friction plate 28 may be connected to the carrier C. it can. Also in these cases, the torque of the engine 12 can be distributed to the friction clutch transmission force and the gear direct force and transmitted to the load 16, and the fastening force of the friction clutch 20 and the torque of the hydraulic pump 32 (or generator). The torque transmitted from the engine 12 to the load 16 can be adjusted.

“Embodiment 3”
FIG. 8 is a diagram showing a schematic configuration of a power output device including the starting device 10 according to Embodiment 3 of the present invention. In the following description of the third embodiment, the same or corresponding components as those of the first and second embodiments are denoted by the same reference numerals, and redundant description is omitted.

  In the present embodiment, the drive side friction plate 26 of the friction clutch 20 is connected to the carrier C of the planetary gear mechanism 18 as compared with the second embodiment. Therefore, in the engaged state of the friction clutch 20, the carrier C and the sun gear S are coupled via the friction clutch 20, and the rotational freedom degree of the planetary gear mechanism 18 is limited to one degree of freedom.

  Also in the present embodiment, as in the second embodiment, when the friction clutch 20 is in the released state and the torque of the hydraulic pump 32 is adjusted to 0 by the pressure regulating valve 36, the engine 12 transmits the transmission 14 (load The torque transmission to 16) is interrupted. On the other hand, by gradually increasing the fastening force (pressing force) between the driving side friction plate 26 and the driven side friction plate 28 from 0 (engaging the friction clutch 20), the torque of the engine 12 is increased to the carrier C and the friction clutch. 20 can be transmitted to the transmission 14. As a result, torque transmission from the engine 12 to the transmission 14 (load 16) can be allowed, and the load 16 can be driven, such as starting the vehicle. Further, similarly to the second embodiment, the torque of the hydraulic pump 32 is gradually increased from 0 by the drive control of the pressure regulating valve 36, whereby the transmission 14 is received via the sun gear S while receiving the torque of the engine 12 by the hydraulic pump 32. Can be communicated to. This also allows torque transmission from the engine 12 to the transmission 14 (load 16).

  When power is transmitted from the engine 12 to the load 16 by engaging the friction clutch 20 and generating torque in the hydraulic pump 32, the power of the engine 12 is transmitted to the friction clutch 20 and the sun gear S as shown in FIG. And the ring gear R (hydraulic pump 32). Then, the power distributed to the sun gear S and the power transmitted via the friction clutch 20 are combined on the input side of the transmission 14, and the combined power is shifted by the transmission 14 and then applied to the load 16. Communicated.

  When the torque of the hydraulic pump 32 (torque acting on the ring gear R) is Tpump, the torque acting on the sun gear S is ρ × Tpump, as shown in the collinear diagram of FIG. When the transmission torque of the friction clutch 20 is Tfric, the torque transmitted from the engine 12 to the transmission 14 is Tfric + ρ × Tpump. Therefore, also in this embodiment, by adjusting the torque Tpump of the hydraulic pump 32, the torque ρ × Tpump and Tpump distributed from the engine 12 to the sun gear S and the ring gear R can be adjusted. 14 (load 16) can be adjusted to torque Tfric + ρ × Tpump. The torque Tfric + ρ × Tpump transmitted from the engine 12 to the transmission 14 (load 16) can also be adjusted by adjusting the fastening force (pressing force) of the friction clutch 20.

  Also in this embodiment, the torque of the engine 12 can be distributed to the friction clutch transmission force transmitted through the friction clutch 20 and the gear direct transmission force transmitted through the sun gear S and transmitted to the load 16. . As a result, the torque transmitted by the friction clutch 20 during torque transmission from the engine 12 to the load 16 can be reduced, so that the size of the friction clutch 20 can be reduced. Furthermore, since the torque received by the hydraulic pump 32 during torque transmission from the engine 12 to the load 16 can be reduced, the hydraulic pump 32 can be reduced in size.

  Also in the present embodiment, when the friction clutch 20 slips, that is, when the rotational speed Neng of the engine 12 (carrier C) is higher than the rotational speed Nout of the sun gear S as shown in the collinear diagram of FIG. , The rotational speed Npump of the hydraulic pump 32 is higher than the rotational speed Neng of the engine 12 by the rotational speed difference ρ × (Neng−Nout) corresponding to the rotational speed difference (Neng−Nout). Thus, when the friction clutch 20 is slipping, the flow rate of the oil discharged from the hydraulic pump 32 can be increased by an amount corresponding to the rotational speed difference (Neng−Nout). Therefore, even when the discharge capacity of the hydraulic pump 32 is not increased, oil having a sufficient flow rate for cooling and lubrication can be efficiently supplied to the friction clutch 20 when the friction clutch 20 slips (heat generation). On the other hand, when the friction clutch 20 is not slipped, the planetary gear mechanism 18 is directly connected, and the rotational speed Npump of the hydraulic pump 32 becomes equal to the rotational speed Neng of the engine 12 (and the rotational speed Nout of the sun gear S). As a result, oil at a flow rate corresponding to the rotational speed Neng of the engine 12 can be discharged from the hydraulic pump 32, and therefore, the oil discharged from the hydraulic pump 32 can be discharged from the lubricating portion of the transmission 14 or the forward / reverse switching mechanism 34. Can be supplied to clutches and brakes.

  In the present embodiment, a preferred specific example of driving the load 16 (starting the vehicle) by controlling the fastening force of the friction clutch 20 and the torque of the hydraulic pump 32 by the electronic control unit 42 will be described. The control described in Embodiment 2 can be applied.

  Also in this embodiment, a generator can be connected to the ring gear R of the planetary gear mechanism 18 as a driven machine. Also in this case, when torque is transmitted from the engine 12 to the load 16, the torque shared by the friction clutch 20 and the generator can be reduced, and the friction clutch 20 and the generator can be reduced in size. When the friction clutch 20 slips, the amount of power generated by the generator (generated power) can be increased by an amount corresponding to the rotational speed difference (Neng-Nout) between the engine 12 and the sun gear S.

  In this embodiment, the hydraulic pump 32 (or generator) is connected to the sun gear S of the planetary gear mechanism (single pinion type planetary gear mechanism) 18, and the driven friction plate 28 of the transmission 14 and the friction clutch 20 is connected to the planetary gear. It can also be connected to the ring gear R of the gear mechanism 18. In this case as well, the torque of the engine 12 can be distributed to the friction clutch transmission force via the friction clutch 20 and the gear direct force via the ring gear R and transmitted to the load 16, and the fastening force of the friction clutch 20 can be transmitted. The torque transmitted from the engine 12 to the load 16 can be adjusted by adjusting the torque of the hydraulic pump 32 (or the generator).

  Also in the present embodiment, the planetary gear mechanism 18 can also be configured by a double pinion type planetary gear mechanism. In this case, the engine 12 and the driving side friction plate 26 are connected to the ring gear R, the hydraulic pump 32 (or generator) is connected to the carrier C, and the transmission 14 and the driven side friction plate 28 are connected to the sun gear S. . Alternatively, the engine 12 and the drive side friction plate 26 may be connected to the ring gear R, the hydraulic pump 32 (or generator) may be connected to the sun gear S, and the transmission 14 and the driven side friction plate 28 may be connected to the carrier C. it can. Also in these cases, the torque of the engine 12 can be distributed to the friction clutch transmission force and the gear direct force and transmitted to the load 16, and the fastening force of the friction clutch 20 and the torque of the hydraulic pump 32 (or generator). The torque transmitted from the engine 12 to the load 16 can be adjusted.

  In the first to third embodiments described above, the case where the engine 12 is used as the prime mover has been described. However, a motor may be used as the prime mover.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and it can implement with a various form in the range which does not deviate from the summary of this invention. Of course.

It is a figure which shows schematic structure of a motive power output device provided with the starting apparatus which concerns on Embodiment 1 of this invention. It is an alignment chart explaining operation | movement of the start apparatus which concerns on Embodiment 1 of this invention. It is a figure explaining operation | movement of the starting apparatus which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of a power output device provided with the starting apparatus which concerns on Embodiment 2 of this invention. It is an alignment chart explaining operation | movement of the start apparatus which concerns on Embodiment 2 of this invention. It is a figure which shows the relationship of the rotational speed Npump of a hydraulic pump with respect to the speed ratio e of the rotational speed Nout of a sun gear, and the rotational speed Neng of an engine. It is a figure which shows the structural example which accepts the torque transmission from an engine to a load by receiving the torque of an engine with a hydraulic pump. It is a figure which shows schematic structure of a power output device provided with the starting apparatus which concerns on Embodiment 3 of this invention. It is a figure explaining operation | movement of the starting apparatus which concerns on Embodiment 3 of this invention. It is an alignment chart explaining operation | movement of the starting apparatus which concerns on Embodiment 3 of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 Starting device, 12 Engine, 14 Transmission, 16 Load, 18 Planetary gear mechanism, 20 Friction clutch, 26 Driving side friction plate, 28 Driven side friction plate, 32 Hydraulic pump, 34 Forward / reverse switching mechanism, 36 Pressure regulating valve, 42 Electronic control unit, C carrier, R ring gear, S sun gear.

Claims (11)

A starting device that drives a load by allowing torque transmission from the prime mover to the load,
Torque distributed to the third rotating member includes a first rotating member to which torque from the prime mover is transmitted, and a second rotating member and third rotating member to which torque transmitted to the first rotating member is distributed. A torque distribution mechanism that transmits
A first fastening member coupled to the second rotating member; and a second fastening member coupled to the third rotating member; and adjusting the fastening force between the first fastening member and the second fastening member from the prime mover. A clutch capable of adjusting the torque distributed to the second rotating member and the third rotating member;
With
By adjusting the fastening force between the first fastening member and the second fastening member, the torque transmitted from the prime mover to the load is adjusted , and further, the torque transmitted from the prime mover to the load is changed from the first rotating member to the first rotational member. A starting device that is distributed to a torque that is distributed to the two rotating members and transmitted to the load via the clutch, and a torque that is distributed from the first rotating member to the third rotating member and transmitted to the load . The starting device according to claim 1,
A driven machine connected to the second rotating member, the driven machine capable of adjusting the torque distributed from the prime mover to the second rotating member and the third rotating member by adjusting the torque;
A starting device in which the torque transmitted from the prime mover to the load is adjusted by adjusting the torque of the driven machine. A starting device that drives a load by allowing torque transmission from the prime mover to the load,
Torque distributed to the third rotating member includes a first rotating member to which torque from the prime mover is transmitted, and a second rotating member and third rotating member to which torque transmitted to the first rotating member is distributed. A torque distribution mechanism that transmits
A first fastening member coupled to the first rotating member; and a second fastening member coupled to the third rotating member, wherein the load from the prime mover is adjusted by adjusting a fastening force between the first fastening member and the second fastening member. A clutch capable of adjusting the torque transmitted to
A driven machine connected to the second rotating member, the driven machine capable of adjusting the torque distributed from the prime mover to the second rotating member and the third rotating member by adjusting the torque;
With
The torque transmitted from the prime mover to the load is adjusted by adjusting the fastening force between the first fastening member and the second fastening member and the torque of the driven machine. The starting device is distributed between the torque transmitted to the load via the first torque and the torque distributed from the first rotating member to the third rotating member and transmitted to the load . The starting device according to claim 2 or 3,
When the rotational speed of the first rotating member is higher than the rotational speed of the third rotating member, the torque distribution mechanism is configured such that the rotational speed difference corresponding to the rotational speed difference and the rotational speed of the second rotating member are the first rotating member. A starting device that is a differential mechanism that is higher than the rotational speed of the vehicle. The starting device according to any one of claims 2 to 4,
A starting device that prioritizes increasing the torque of the driven machine over increasing the fastening force between the first fastening member and the second fastening member when increasing the torque transmitted from the prime mover to the load. The starting device according to claim 5,
A starting device for increasing the torque of the driven machine without fastening the first fastening member and the second fastening member when the required torque of the load is not more than a set value when increasing the torque transmitted from the prime mover to the load. . The starting device according to claim 5 or 6,
When the torque transmitted from the prime mover to the load is increased and the required torque of the load is larger than the set value, the fastening force between the first fastening member and the second fastening member is generated in a state where the torque is generated in the driven machine. Increase the starting device. The starting device according to any one of claims 2 to 7,
The driven machine is a hydraulic pump that sucks and discharges oil,
A starting device comprising adjusting means for adjusting a torque of a hydraulic pump by adjusting a discharge pressure of oil from the hydraulic pump. The starting device according to claim 8,
A starting device in which oil discharged from a hydraulic pump is supplied to a clutch. A starting device according to any one of claims 1 to 9,
The torque distribution mechanism is a single pinion type planetary gear mechanism including a sun gear, a carrier, and a ring gear.
The starting device, wherein the first rotating member is a carrier, the second rotating member is one of a sun gear and a ring gear, and the third rotating member is the other of the sun gear and the ring gear. A starting device according to any one of claims 1 to 9,
The torque distribution mechanism is a double pinion type planetary gear mechanism including a sun gear, a carrier, and a ring gear.
The starting device, wherein the first rotating member is a ring gear, the second rotating member is one of a sun gear and a carrier, and the third rotating member is the other of the sun gear and the carrier.

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