JPS62147148A - Hydraulic continuously variable transmission - Google Patents

Abstract

PURPOSE:To smoothly perform a change over between advance and reverse by disposing a reverse gear train between a mechanical system torque output part and a mission output part in the low range of a differential gear mechanism. CONSTITUTION:In the case of reverse, a low clutch 16 and a high clutch 18 are turned on, a reverse clutch 27 is turned on, an input torque is distributed to a hydraulic system and a mechanical system torque is transmitted from a ring gear 10 through transmitting gears 13 and 14 in the same way as in the case of a low range, a second unit 5 operates as a pump, and a first unit 4 as a motor. A mechanical system torque is transmitted to a transmitting gear 11 from a sun gear 7, joined hereat with a hydraulic system torque transmitted through a transmitting gear 12 in the same direction of rotation, and transmitted to a final reduction gear 19 through a gear 25, a reverse shaft 24, a clutch 27, gears 26, 28 and 17. These can smoothly perform a change over to reverse, and improve torque transmission efficiency.

Description

[Detailed Description of the Invention] (1) Fields of Application of the Invention The present invention relates to a hydraulic continuously variable transmission, and in particular, the present invention relates to a hydraulic continuously variable transmission, and in particular, the present invention relates to a hydraulic continuously variable transmission. It's about Esurura.

(Prior Art) Conventionally, this type of hydraulic continuously variable transmission is known, for example, as disclosed in U.S. Pat. and a differential m-wheel mechanism that distributes the input torque to the hydraulic system torque by the pump & motor unit [•], and the differential tooth width) that can transmit one herk per different request of one structure. A low clutch and a high clutch are connected, and the low clutch and high clutch are connected/disconnected between the low range and the high range, and the discharge amount of the pump & motor unit 1 of the above II] is changed in each range, thereby changing the speed. Continuously and steplessly (qru J: It is known that 6 of the sea urchins are carried out continuously and steplessly.

(Problems to be Solved by the Invention) By the way, in the conventional continuously variable transmission described above, in the case of reverse, the Tanabata side unit in the case of low range is reversely rotated, and the It is configured to use hydraulic torque to transmit drive torque in the opposite rotational direction to the wheels when in the low range.

However, in this case, the hydraulic system torque and the mechanical system torque are in opposite rotational directions, and the mechanical system torque acts as resistance against the hydraulic system torque, resulting in a large drive torque loss and poor efficiency. There was a problem.

The present invention has been made in view of the above, and its purpose is to improve the torque transmission system for reverse in a hydraulic continuously variable transmission as described above, and to improve the torque transmission system in the same rotational direction. By transmitting the driving torque in the forward direction (low range or high range) and in the reverse rotation direction to the wheels using torque and torque, the loss of driving torque is reduced and efficiency is increased. It is about increasing.

Another object of the present invention is to improve the torque transmission system in the case of reverse as described above, by making it unnecessary to switch the operation of the pump source motor unit 1 and 71 when switching between forward and reverse. The aim is to make the process smoother.

(Means for Solving the Problems) In order to achieve the above object, the solving means of the present invention uses a hydraulic continuously variable transmission system, a variable displacement pump & one unit, and an input unit. A differential tooth width mechanism that distributes the torque to the hydraulic torque of the pump & motor unit 1 and the punching system 1, and 1 to the different elements of the differential tooth qX mechanism.
It is assumed that the present invention is equipped with a low clutch and a high clutch that are connected to enable transmission of torque and switch between a low range and a high range.

In such a hydraulic continuously variable transmission, a reverse gear train consisting of a reverse idle gear, a reverse clutch, etc. is provided between the low range mechanical torque output section of the differential tooth width mechanism and the transmission output section. The configuration is such that the

(Function) With the above configuration, in the present invention, in the case of reverse, when the reverse clutch of the reverse gear train is connected, one set of Of the pump & motor units 1 to 1, the mechanical torque transmitted from the motor-side unit that operates the motor to the mechanical torque output section and the hydraulic torque in the same rotational direction as in the case of the low range are transmitted to the reverse gear train. The rotational direction is reversed in the reverse gear (adren) and transmitted to the transmission output section, so that the driving torque in the opposite rotational direction to that in the case of forward movement is transmitted from the transmission output section to the wheels.

However, in the case of this reverse mode, the pump and motor unit h operates the pump or motor in the same way as in the case of the low range when switching between forward and reverse, so when switching between forward and reverse, There is no need to switch the operation of the pump source motor unit, and the switching can be done smoothly.

(Example) Embodiments of the present invention will be described below based on the drawings.

1 to 4 show a hydraulic continuously variable transmission according to an embodiment of the present invention. In Figure 1, there is J3, 1 is the casing,
2B is a primary shaft 1j rotatably disposed within the casing 1, and one end of the primary shaft 2 is drivingly connected to an output shaft 40 of the engine via a clutch 3. 4 and 5 are variable displacement one-phase first and second pumps and seven units (hereinafter referred to as the first and second pumps).
The rotational axes /Ia and 5a of both the units 1 to 4.5 are arranged parallel to the bridle press A1 and the shaft 2, respectively.

The primary shirts 1 and 2 have an engine output shaft 40
The input torque from the above first J5 and second unit 1-1
An idle differential gear mechanism 6 is installed for distributing the hydraulic system 1 and 1 (acid system I~LUK) according to 5, and the Ti star differential gear □ (l, i 5 is primary shirt 1
-2, a pair of plane gears t79.9 which are rotatably supported by the plane gear A77, which mesh with the plane gear 7 and are fixedly supported by the primary shaft 2 via the kitria 8, and the plane tree Vs7'), 9, etc. The first transmission gear 11 is integrally provided with the ring gear ψ7, and the first transmission gear 711 is fitted into the rotation @4a of the first unit 4. The ring gear 1o meshes with the second transmission gear 12.
It is connected to a third transmission gear A713 rotatably supported by the primary shaft 2, and the third transmission gear r13 is
A fourth unit fixedly supported on the rotating shaft 5a of the second unit 5
It meshes with the transmission gear 14.

Further, a fifth transmission gear A715 is rotatably supported on the rotation shaft 4a of the first unit 4, and the fifth transmission gear A715 is connected to the low clutch 16 with respect to the rotation shaft 4a of the first unit 4.
The sixth transmission gear 17 is connected to the primary shaft 2 via the primary shaft 2, and meshes with the sixth transmission gear 17 rotatably supported by the primary shaft 2. The sixth transmission gear 17' is a ring gear 10 of the third transmission gear 13 or the horizontal six of the fl star-shaped gear machine.
The high clutch 18 is connected to the high clutch 18. Both the low clutch 16 and the high clutch 18 are hydraulic clutches, and the low clutch 16 is located on the rotating shaft 4a of the first unit 4, and the high clutch 18 is located on the brake shirt 1-2. Place it in the state
are doing.

As shown in FIGS. 2 and 3, the sixth transmission gear 'X717 meshes with one final reduction gear 45, and a final pinion gear 20 is coaxially integrated with the reduction gear 1-19. The gears t19, 20 are rotatably supported by the cushioning 1. The above final pinion gear i720 is
It meshes with the final ring gear 22 fixed to the case 21a of the differential device 21, and the final ring gear \
The driving torque transmitted to the IFJJ device 21
From the drive shaft 23.23 to the left and right wheels (
(not shown).

Furthermore, in FIG. 4, reference numeral 24 denotes a reverse shaft rotatably arranged in parallel with the primary shaft 2 within the casing 1, and the reverse shaft 24 has a first transmission gear 11 on the primary shaft 2. A first reverse gear 725 that meshes with the reverse shaft 24 is formed integrally with the second reverse gear! 26 is rotatably supported. The second reverse gear 26
is reverse clutch 2 for reverse shirt 1-24.
7, and meshes with the sixth transmission gear 1'/17 on the primary shaft 2 via a reverse idle gear 28 (see FIG. 2). Therefore, in the case of reverse, the first transmission gear 1 on the primary shaft 2
1 (mechanical system torque output section in the low range of the planetary differential gear mechanism 6), reversely converts its rotational direction and transmits it to one final reduction gear, which is the mission output section. It consists of two lenses. In addition, in Fig. 1, 31 is the low clutch 1G.
This is an overdrive brake located on the outer periphery of the

Next, the operation of the above-mentioned hydraulic continuously variable transmission will be explained using FIGS. 5 to 7.

FIG. 5 shows the path of one herk in the case of low range. In the case of this low range, the low clutch 16, high clutch 18 and reverse Clara f
Only the rear low clutch 16 of ~27 is connected, and the low clutch 18.27 is disconnected. The input torque from the engine output shaft is transmitted via the primary shaft 2 to the planetary gear V9 side of the I11 differential gear mechanism 6, and the planetary differential gear mechanism 6 causes the hydraulic system [. (corresponding to the broken line) and mechanical torque (corresponding to the thin broken line in the figure). Hydraulic system torque is transmitted from the ring gear 1710 of the power foot differential gear mechanism 6 to the third and fourth transmission gears 1.
3.14 to the rotating shafts 5a of the second units 1-5, whereby the second units 1-5 operate as pumps, and the first unit 4 receives the discharge from the second units 1-5. It operates as a regulator by receiving the pressurized oil. On the other hand, the mechanical torque is 6 t number V77 to the planetary differential gear h'.
From the 1st J: and the 2nd Buddha Gi 1711.12,
As described above, it is transmitted to the rotary sleeve 4a of the first unit 4, which operates the motor, and joins the hydraulic system 1. This merged drive f) J I-luk is from the low clutch 1G to the 5th. The signal is transmitted to the final reduction gear 19 (small wheel side) via the sixth transmission gear 15.17.

Further, FIG. 6 shows the transmission path of torque in the case of the high range. In the case of the high range, only the high clutch 18 is connected, and the low clutch 16 and reverse clutch 27 are disconnected. And input (
.about.luk is distributed between the hydraulic system 1.about.luke and the mechanical system torque by the planetary differential gear mechanism 6, as in the case of the low range described above. Hydraulic torque is transmitted from the Mu differential middle wheel mechanism 6 to the rotating shaft 4a of the first unit 4 via the first and second transmission gears 11.12, thereby causing the first unit to rotate. 4 operates as a pump, and the second unit 5
receives the pressure oil discharged from the first unit 4 and operates as a motor. On the other hand, the mechanical system 1 to
Jll! The rotation is transmitted from the ring gear A710 of the IL wheel mechanism 6 to the third transmission gear ψ13, and the second unit that operates the motor as shown above) rotates from the rotation @5a of 5 to the third transmission gear A via the fourth transmission gear 14. ? It merges with the hydraulic system torque transmitted to 13. This combined driving torque is transmitted to the high clutch 18
is transmitted to one final reduction gear via the sixth transmission gear 17.

In the case of the above-mentioned low range Ji J: and high range, the hydraulic discharge amount of the first and second units h4 and 5 is adjusted to vary the transmission rate of the hydraulic system torque between the two units 1 to 4.5. In addition, the distribution of the hydraulic system torque in the 'fJ differential gear II mechanism 6 to the yarn torque is changed by switching between the connection and disconnection of the clutch 6 and the high clutch 18, that is, switching between the low range and the high range. This allows gear changes to be performed continuously and steplessly.

Furthermore, FIG. 7 shows the l~silk transmission path in the case of reverse. In this reverse case, [
”-Clutch 16 and high clutch 18 are both disengaged and only reverse clutch 27 is engaged. and,
The input torque is divided into the hydraulic system torque and the yarn torque by the first differential tooth single mechanism 6, and the hydraulic system torque is distributed to the link gear 1 of the TL star differential gear mechanism 6 as in the case of the low range described above. 3rd and 4th transmission gear 13.1
4 to the rotating shaft 5a of the second unit 5, the second unit 5 operates as a pump, and the first unit 4 operates as a motor. On the other hand, mechanical torque is
The sun gear 7 of the yi star differential gear mechanism 6 and the first transmission gear 1
In Egya 11, the above-mentioned
After the rotation shaft 4a of the unit 4 merges in the same rotational direction with the hydraulic system 1 to torque transmitted via the second transmission gear 12, the rotation shaft 4a of the unit 4 is connected to the reverse shaft 24 via the first reverse gear 25.
transmitted to.

The driving torque transmitted to the reverse gear 11 and the shaft 24 is transmitted from the reverse clutch 27 to the final reduction gear via the second reverse gear ψ26, the reverse idle gear 728, and the sixth transmission gear 17, in the opposite manner to the case of the low range and high range. It is transmitted as torque in the direction of rotation.

In this way, in the case of reverse, the planetary differential tooth width mechanism 6
The mechanical system (herc and hydraulic system torques) are connected to the first transmission gear 1711 integrated with the Sangi V7, which is the mechanical system torque output section in the low range, and the mechanical system (Herc and hydraulic system torques) merge in the same rotation direction, and this combined drive torque is transmitted to the reverse gear train 2. In the low range J5 and high range, that is, in the case of forward movement, the torque is transmitted to the final reduction gear A719, which is the mission output part, through the gear ITV clutch, etc. can be significantly reduced compared to the conventional case, and the efficiency of (can be significantly increased).

Moreover, in the case of this reverse, the first J5 and the second units 1 to 4, 5 are switched to the second unit 1, as in the case of the low range, in which 1) reverse is changed in particular.
5 operates the pump, and the first T units 1 to 4 operate the exhaust, so when switching between 11) forward and reverse, it is necessary to switch the operation of both units 4.5. Therefore, it is possible to make the switching smoother.

Here, the change 1 in the hydraulic discharge a with respect to the gear ratio of the first and second units 1-4 and 5? An example of the J property is shown in FIG. Regarding the change characteristics in Fig. 8, a3 indicates that when the gear ratio is zero at the time of switching between reverse and forward mode, the hydraulic pressure output of the first units 1 to 4 is constant at the maximum discharge amount. In addition, only the oil pressure rL output amount of the second unit 5 is set to change as the gear ratio increases or decreases, but the change does not change stepwise but continuously. , it can be seen that switching between forward and reverse is performed smoothly.

It should be noted that the present invention is not limited to the above embodiments, but includes various other modifications.

For example, in the above embodiment, the present invention was applied to a case where a star gear mechanism was used as a differential tooth 4I mechanism that distributes input torque into hydraulic system torque and mechanical system torque, but there are various other differences. Of course, the present invention can also be similarly applied to a case where a moving float mechanism is used.

Furthermore, the low clutch 16 and high clutch 18 for changing the torque distribution by the differential float mechanism are not limited to being arranged in a biaxial state as in the above embodiment, but may be arranged in a coaxial state. can also be applied.

(Effects of the Invention) As described above, according to the hydraulic continuously variable transmission of the present invention, a reverse gear train is disposed between the mechanical torque output section and the transmission output section in the low range of the differential float mechanism. Therefore, in the case of reverse, the mechanical system torque and the hydraulic system torque in the same rotational direction from the Since the torque is transmitted to the wheels as directional torque, it is possible to reduce drive torque transmission loss and increase efficiency.Moreover, in the case of this reverse, the one-phase pump & motor unit can switch between forward and reverse. As in the case of low range, the pump operation E) + or the motor operation U'' is used, so there is no need to switch the operation of the pump & motor unit l- when switching between forward and reverse, making the switching smoother. I can do it.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention, and Fig. 1 is a sectional view of a hydraulic continuously variable transmission, and Fig. 2 shows the meshing states of various gears as seen along the line Figures 3 and 4 showing
The figures are respectively I[[-I[[ line and TV-
FIG. 4 is a cross-sectional view of IV Fii. FIG. 5 is a schematic diagram showing the torque transmission path in the case of [1-range], FIG. 6 is a diagram equivalent to FIG. 5 in the case of high range, and FIG. 7 is a diagram equivalent to FIG. 5 in the case of reverse, FIG. 8 is a diagram showing the change characteristics of the hydraulic discharge amount of the pump & motor unit 1. 4...First unit, 5...Second unit t-16.
...Planetary differential gear mechanism, 16...Low clutch, 18
...High clutch, two...reverse gear train. Before joining the agency 1)
Hirozumasa - 8-5/1 Figure 4 Figure 5 Figure 6 Figure 7 Figure 8 Hatsugaki Yu

Claims (1)

[Claims] (1) A variable displacement pump and motor unit,
A differential gear mechanism that distributes the input torque into hydraulic torque and mechanical torque generated by the pump and motor unit; and a differential gear mechanism that is connected to different elements of the differential gear mechanism so as to transmit torque, and switches between a low range and a high range. In a hydraulic continuously variable transmission equipped with a low clutch and a high clutch, a reverse gear drain is disposed between the mechanical torque output section and the transmission output section in the low range of the differential gear mechanism. Hydraulic continuously variable transmission.