JPH034854Y2 - - Google Patents

Description

[Detailed explanation of the idea] [Industrial application field]

The present invention relates to a double-row continuously variable transmission, and in particular,
The present invention relates to an improvement in a double-row continuously variable transmission device that includes at least two rows of so-called belt-type continuously variable transmission mechanisms arranged in parallel between an input shaft and an output shaft.

[Conventional technology]

A belt-driven continuously variable transmission mechanism is one type of automatic transmission mechanism for vehicles. This continuously variable transmission mechanism generally has a V-shaped pulley device on an input shaft and an output shaft, respectively, which consists of a fixed pulley and a movable pulley and whose effective diameter is variable by a hydraulic device. The rotation of the input shaft can be transmitted to the output shaft in a stepless manner by means of a transmission belt stretched between the two. This type of continuously variable transmission mechanism has fewer sudden changes in driving force during driving than an automatic transmission mechanism that consists of a combination of a so-called torque converter and a planetary gear set, has a smaller shift shock, and is more fuel efficient. However, due to its durability, the torque transmission capacity of the belt is relatively small.
Conventionally, they have generally been used for small displacement automobiles. However, such advantages such as small shift shocks and high fuel efficiency are advantages that are required for large-displacement automobiles, and therefore there is a need to develop continuously variable transmissions with larger torque transmission capacity. This is a growing social demand. Technologies to meet this demand include technologies that focus on improving the durability of the belt itself, as well as technologies that increase the total transmitted torque by arranging two or more rows of continuously variable transmission mechanisms in parallel between the input and output shafts. Techniques have been devised to increase this speed, and automobiles have been put into practical use that are equipped with a double-row continuously variable transmission on the rear axle that utilizes the tensile force of a dry rubber belt.

[Problem that the invention attempts to solve]

However, such conventional double-row continuously variable transmissions have had problems in that the structure has become more complex, the device has become larger, and its weight has also increased. In particular, in order to ensure a large torque transmission capacity for applications in automobiles equipped with large-displacement engines, a double-row continuously variable transmission that uses the pressing force of a wet metal belt is the best. When such a double-row continuously variable transmission using a wet metal belt is adopted, there is a problem that the size and weight increase further.

[Purpose of invention]

The present invention has been made in view of these conventional problems, and an object of the present invention is to provide a double-row continuously variable transmission device that has a simple structure, is smaller in size, and can be reduced in weight.

[Means to solve the problem]

The present invention has a V-shaped pulley device on the input shaft and the output shaft, respectively, which consists of a fixed pulley and a movable pulley and whose effective diameter is variable by a hydraulic device.
A belt-type continuously variable transmission mechanism capable of steplessly transmitting the rotation of the input shaft to the output shaft by means of a transmission belt stretched between the V-type pulley device, is provided between the input shaft and the output shaft. In a double-row continuously variable transmission having at least two rows in parallel between the input shaft and the output shaft, one hydraulic chamber is shared between adjacent V-type pulley devices on at least one side of the input shaft and the output shaft. The above object has been achieved by installing a hydraulic system for driving both movable pulleys. Further, in an embodiment of the present invention, a hydraulic device sharing the hydraulic chamber is installed only on the output shaft side, and a hydraulic device having an independent hydraulic chamber is installed in each case on the input shaft side. This is designed to prevent slips and the like that occur due to variations in the continuously variable transmission mechanisms of each row.

[Effect]

In the present invention, between the adjacent V-type pulley devices on at least one side of the input shaft and the output shaft,
Because the hydraulic system for driving both movable pulleys, which share one hydraulic chamber, is installed, compared to driving each movable pulley of each V-type pulley device with an independent hydraulic system, the number of hydraulic devices is reduced accordingly. Equivalent performance can be maintained in the hydraulic chamber. Therefore, since the hydraulic chamber is omitted, it is possible to achieve a reduction in size and weight.

【Example】

Embodiments of the present invention will be described in detail below based on the drawings. 1 and 2 show an embodiment of a double-row continuously variable transmission for an automobile to which the present invention is applied. This continuously variable transmission device includes a fluid coupling section 1, belt type continuously variable transmission sections A and B, a planetary gear section 2 for forward/reverse switching,
It is mainly composed of a reduction gear part 3 and a differential gear part 4. The fluid coupling section 1 transmits the rotational power of the engine to the input shaft via fluid, and even if there is a difference between the engine rotational speed and the vehicle speed when the vehicle starts or stops, it smoothly compensates for this difference. It is for transmitting power while absorbing power into the engine, and is equipped with a lock-up clutch 1a. The belt-type continuously variable transmission units A and B are arranged in parallel on the input shaft and the output shaft, and each includes V-type pulley devices 10A, 20A, 10B, and 20B. Each V-type pulley device 10A, 2 of the continuously variable transmission section A
0A is composed of fixed pulleys 11A, 21A and movable pulleys 12A, 22A, respectively, and when the movable pulleys 12A, 22A slide along the axial direction of the first input shaft 102 or the output shaft 20, the fixed pulley and the movable The effective diameter can be changed by changing the width of the V-groove formed between the pulleys. Moreover, these V-type pulley devices 10A, 20
A transmission belt 30A is stretched between A, and rotational torque is transmitted from the input shaft side to the output shaft side at a stepless speed ratio according to changes in the effective diameter of both V-type pulley devices 10A and 20A. I'm starting to be able to do it. On the other hand, the belt-type continuously variable transmission section B also has basically the same configuration as the belt-type continuously variable transmission section A,
Fixed pulleys 11B, 21B and movable pulleys 12 are provided on the second input shaft 104 side and the output shaft 20 side, respectively.
V-type pulley device 10B, 20 consisting of B, 22B
B, and a transmission belt 30B is stretched between both V-type pulley devices 10B and 20B to perform continuously variable speed. In this embodiment, in such a double-row continuously variable transmission, the movable pulleys 22A,
A hydraulic device 50 for driving both movable pulleys 22A and 22B is installed, with the two movable pulleys 22A and 22B disposed facing each other and sharing one hydraulic chamber 52 therebetween. That is, the V-type pulley devices 10A, 10 on the input shaft side
B is provided with hydraulic devices 40A and 40B having exclusive hydraulic chambers 42A and 42B for driving the movable pulleys 12A and 12B, but the V-type pulley devices 20A and 20B on the output shaft 20 side are teeth,
Only one hydraulic device 50 sharing a hydraulic chamber 52 is disposed between them, and both movable pulleys 22A, 22
B are simultaneously driven by a single control signal. Note that the input shaft has a first input shaft 102 and a second input shaft.
and an input shaft 104, each of which is spline-coupled so that they can rotate together. That is, the first input shaft 102 has a ball bearing 106,
The second input shaft 10 is supported by a sliding bearing 108.
4 are supported by a ball bearing 110 and a roller bearing 112, and are arranged coaxially with each other. The output shaft 20 is a belt type continuously variable transmission section A, B.
Commonly used, ball bearing 202 and roller bearing 20
4, the first and second input shafts 102,1
It is arranged parallel to 04. As shown in detail in FIG. 3, this output shaft 20 has rows A and B.
A torque detection device 60 including resistance wire strain gauges 60A and 60B is provided near each of the fixed pulleys 21A and 21B in the row, and the strength and weakness of rotational torque near both fixed pulleys 21A and 21B of the output shaft 20 is determined by conduction. Bands 61A, 61B and brush 62A,
62B. Further, the V-type pulley device 10A, 1 on the input shaft side
The fixed pulleys 11A and 11B of 0B are arranged to face each other, and are arranged opposite to the V-type pulley devices 20A and 20B on the output shaft 20 side, respectively. The reason why the axial arrangement of the fixed pulley and the movable pulley on the input/output side is reversed for each row A and B is that the sliding of each movable pulley allows the V-type pulley device to This is so that the transmission belts 30A, 30B can always maintain a state perpendicular to the input/output shaft even if the effective diameter changes. The hydraulic devices 40A and 40B on the input shaft side are formed symmetrically with respect to the V-type pulley devices 10A and 10B, respectively. That is, this hydraulic system 40
A, 40B are integrally extended and formed with the movable pulleys 12A, 12B, and the first and second input shafts 102,
Cylinder 41 movable in the axial direction of 104
A, 41B, and a piston 43 defining hydraulic chambers 42A, 42B together with the cylinders 41A, 41B.
It is mainly composed of A and 43B. Then, from the hydraulic pump 70 to the oil passages 44A, 45A, or 44B, 4
When hydraulic pressure is supplied to the hydraulic chambers 42A, 42B via the hydraulic pressure chambers 5B, the cylinders 41A, 41B integrated with the movable pulleys 12A, 12B can move relative to the pistons 43A, 43B. The cylinders 41A, 41B integrally formed with the movable pulleys 12A, 12B are the first,
Ball 46 with respect to second input shaft 102, 104
A and 46B (FIG. 1) are spline-engaged to allow axial sliding. On the other hand, movable pulleys 22A, 22 on the output shaft 20 side
A hydraulic device 50 for driving B has a cylinder 51 that extends and is formed integrally with the movable pulley 22A of the A row, and a cylinder 51 that extends and is formed integrally with the movable pulley 22B of the B row. together with hydraulic chamber 5
2 and a piston 53 that separates the piston 53 from each other.
By supplying hydraulic pressure from the hydraulic pump 70 to the hydraulic chamber 52 through the oil passages 54 and 55, the cylinder 51 and piston 53 are driven simultaneously and symmetrically, forcing the effective diameter of the input shaft side. Changes in the effective diameter on the output shaft side can smoothly follow changes. The cylinder 51 and piston 53 are spline-engaged with the output shaft 20 via balls 56 and 57, so that they can slide in the axial direction. In FIG. 1, the housings include an accelerator case 91 and a first transmission case 9.
2. Consisting of an intermediate case 93 and a second transmission case 94, the roller bearing 112 is comprised of an intermediate case 93 and a second transmission case 94.
installed on. Further, the planetary gear unit 2 for forward/reverse switching is equipped with a Ravignio type compound planetary gear mechanism, and obtains two forward speeds and one reverse speed by selectively operating two brakes and one clutch. . Further, the deceleration gear section 3 is for decelerating the output of the forward/reverse switching planetary gear section via an intermediate gear, and the differential gear section 4 is for decelerating the output of the forward/reverse switching planetary gear section via an intermediate gear.
The output is transmitted to the left and right wheels of the vehicle in a state that allows differential rotation. The planetary gear section 2 for forward/reverse switching, the gear section 3 for reduction, and the differential gear section 4 are not particularly different from conventionally known ones, and detailed explanations thereof will be omitted. Next, FIG. 4 shows a main part of the hydraulic circuit of the double-row continuously variable transmission. In the figure, 70 is a hydraulic pump, 71 is a relief valve for regulating the output hydraulic pressure of the hydraulic pump to line pressure, and 72 is a first relief valve for regulating the oil flow rate to the hydraulic chamber 42A of the A-row hydraulic device 40A. The flow rate adjustment valve 73 is a second valve for adjusting the oil flow rate to the hydraulic chamber 42B of the hydraulic device 40B in the B row.
It is a flow rate adjustment valve. As is clear from the figure, the line pressure regulated by the relief valve 71 is separately and independently supplied to the hydraulic chambers 42A, 42B on the input shaft side of the A row and B row via both flow rate adjustment valves 72, 73. Supplied. On the other hand, on the output shaft side, a common hydraulic chamber 5
2 is supplied directly. Next, the operation of this embodiment will be explained. The line pressure generated by the hydraulic pump 70 and regulated by the relief valve 71 is transmitted through the oil passage 54,
55 and is applied to the hydraulic chamber 52 of the output side hydraulic device 50. On the other hand, the flow rate of oil in the hydraulic chamber 42A of the input side hydraulic device 40A is controlled by the first flow rate regulating valve 72, and is supplied via the oil passages 44A and 45A.
As a result, the movable pulleys 12A in the A row are driven to have an effective diameter corresponding to the target gear ratio. or,
The flow rate of oil in the hydraulic chamber 42B of the B-row hydraulic device 40B is similarly controlled by the second flow rate regulating valve 73, and is supplied via the oil passages 44B and 45B. As a result, the movable pulleys 12B in row B are also driven to have an effective diameter corresponding to the target gear ratio. In this embodiment, the reason why the flow rate can be controlled for each of the A and B rows is as follows. That is, in this embodiment, belt-type continuously variable transmission parts A and B are of the same type in terms of characteristics.
Ideally, the opening degrees of the flow rate regulating valves 72 and 73 of both transmission sections A and B are the same. However, in reality, there are various variations such as installation errors, belt circumference errors, and differences due to changes over time. A difference (imbalance) may occur in the transmission torque of the B row, or in the worst case, slippage may occur in the transmission belts 30A, 30B of either the A row or the B row. Therefore, in order to avoid this phenomenon, the movable pulleys 12A, 1 on the input shaft side
2B can be controlled separately and independently, so that either of the continuously variable transmission parts A and B can perform the torque transmission function equally without slipping. In this embodiment, in order to perform this control, both fixed pulleys 21A and 21B of the output shaft 20 are used to detect that the transmitted torque is in an unbalanced state or that the continuously variable transmission section on either side is in a slip state.
Detection is performed using the outputs of resistance wire strain gauges 60A and 60B provided nearby. That is, the rotational torque of the first and second input shafts 102 and 104 is transmitted to the output shaft 20 via the continuously variable transmission parts A and B, respectively, but the transmission is performed when the output shaft 20 is on the opposite side to the input shaft side. This is done by receiving rotational torque from a pulley at the semicircular portion. Therefore, the resistance wire strain gauges 60A and 60B generate output waveforms with the same period as the rotational speed of the output shaft 20. The amplitude of this waveform increases as the rotational torque received from the pulley side increases. Therefore, if an imbalance occurs in the transmitted torque or a slip occurs in the continuously variable transmission section on either side, a difference will occur in the amplitude of the output waveforms of the two resistance wire strain gauges 60A and 60B. Therefore, for example, the continuously variable transmission section on the A row side is first set to a target gear ratio according to the vehicle condition, and then the amplitude of the output waveform of the two resistance wire strain gauges 60A and 60B, or the amplitude of the output waveform when the output waveform is smoothed, is If the remaining continuously variable transmission section on the B row side is adjusted so that the accumulated amount per predetermined time is equal, both continuously variable transmission sections A and B can each transmit the same amount of torque without slipping. This will enable you to do this. In the above embodiment, the hydraulic chamber is shared only on the output side, and on the input side, the flow rate is controlled independently for each column to prevent slips in each column and to improve the transmission of each column. The shared torque was distributed equally, but in this invention, for example, when the variations in each row are small and slip etc. can be ignored, or when further miniaturization is required, A configuration may also be adopted in which the side hydraulic chambers are shared. That is, in the above embodiment, by controlling each row on the input shaft side independently, slippage of the transmission belt is prevented and the transmission torque in the continuously variable transmission section of each row is controlled to be equal. However, in the present invention, such control is not necessarily required. Further, in the above embodiments, a device equipped with a two-row continuously variable transmission mechanism was shown, but the present invention does not limit the number of rows of the continuously variable transmission mechanism. That is, the present invention can be applied to a continuously variable transmission having more rows by forming two rows into sets.

[Effect of the idea]

As explained above, according to the present invention, in a continuously variable transmission device having a plurality of continuously variable transmission mechanisms arranged in parallel, the structure can be simplified, and the effect of achieving miniaturization and weight reduction can be obtained. . In particular, excellent effects can be obtained in double-row continuously variable transmissions using wet metal belts, which tend to be larger and heavier.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing the configuration of an embodiment of a double-row continuously variable transmission according to the present invention, FIGS. 2A and B are partially enlarged views of FIG. 1, and FIG. FIG. 4, which is a perspective view showing the output shaft torque detection device in the example, is also a schematic block diagram showing the main part of the hydraulic circuit of the above example. DESCRIPTION OF SYMBOLS 1... Fluid coupling part, 2... Planetary gear part for forward/reverse switching, 3... Reduction gear part, 4... Differential gear part,
A... Belt type continuously variable transmission part of A row, B... Belt type continuously variable transmission part of B row, 102... First input shaft, 1
04...Second input shaft, 10A, 10B...Input shaft side V-type pulley device, 11A, 11B...Fixed pulley, 12A, 12B...Movable pulley, 20...Output shaft, 20A, 20B...Output shaft Side V-type pulley device, 21A, 21B...Fixed pulley, 22A, 2
2B...Movable pulley, 30A, 30B...Transmission belt, 40A, 40B...Hydraulic system, 50...
Hydraulic device (shared in the hydraulic chamber), 51... cylinder,
52... Hydraulic chamber.

Claims (1)

[Claims for Utility Model Registration] (1) A V-shaped pulley device consisting of a fixed pulley and a movable pulley whose effective diameter is variable by a hydraulic device is provided on the input shaft and the output shaft, respectively, and
A belt-type continuously variable transmission mechanism capable of steplessly transmitting the rotation of the input shaft to the output shaft by means of a transmission belt stretched between the type pulley devices is installed between the input shaft and the output shaft. In a double-row continuously variable transmission device having at least two rows in parallel with each other, the double-row continuously variable transmission device is configured such that one hydraulic chamber is shared between adjacent V-type pulley devices on at least one side of the input shaft and the output shaft. A double-row continuously variable transmission device characterized by the installation of a hydraulic device for driving pulleys. (2) A utility model registration request characterized in that a hydraulic device sharing the hydraulic chamber is installed only on the output shaft side, and a hydraulic device having an independent hydraulic chamber for each example is installed on the input shaft side. The double-row continuously variable transmission device according to scope 1.