JPS599781B2 - Output split mechanical-hydraulic transmission with multiple speed ranges - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an output split type mechanical-hydraulic transmission.

In this type of transmission, if you try to achieve a wide speed change range that can be used in automobiles with a single speed range, the horsepower capacity of the hydraulic pump and motor will increase, which will increase cost, increase size, and reduce efficiency. Therefore, a wide shifting range is generally achieved by using multiple speed ranges.

On the other hand, it is advantageous in terms of efficiency and size that the horsepower capacity of the hydraulic pump/motor in this type of transmission is equal to the maximum output of the prime mover.

In a machine-hydraulic transmission system with multiple speed ranges, when the horsepower capacity of the hydraulic pump/motor is made equal to the maximum output of the prime mover, in order to continuously change the speed ratio from zero to 1. It is necessary to divide up to 0 into two speed ranges.

Therefore, when the speed ratio is divided from zero to 1.0 into a first speed range and a second speed range,
In an output split type machine-hydraulic transmission system, when the horsepower capacity of the pair of hydraulic pumps and motors is the same, changing the rotation of the reaction shaft from the upper limit of forward rotation to the upper limit of reverse rotation can widen the speed change range. , a differential gear device exclusively for the first speed range having a reference speed ratio located in the center of the first speed range, and a differential gear device exclusively for the second speed range having a reference speed ratio located in the center of the second speed range. Conventionally, it is a common method to provide

In this method, if the input shaft elements of each differential gear unit are directly connected to the input shaft, the reaction shaft elements of both differential gear units will rotate in opposite directions at the boundary between both speed ranges, making it difficult to switch between both speed ranges. In order to do this smoothly, each reaction force shaft element must be connected via a reversing device.

This not only means that the device becomes more complicated, but also means that the relative rotational speed of the constituent members increases in the frequently used second speed range, which poses a practical problem.

This problem can be solved by setting the reference speed ratio of the differential gear device exclusively for the second speed range to be greater than 1.0, and by interposing a speed reducer between the input shaft element and the input shaft of the differential gear device. However, in this case, the reduction ratio of the reduction gear must be made very large, and considering that the second speed range is frequently used, problems remain in terms of durability and noise.

The present invention attempts to solve all of the above-mentioned problems by simplifying the frequently used differential gear device and power transmission system for the second speed range, and for the first speed range to be used in the second speed range. A differential gear device and a separate differential gear device are used together.

The present invention provides a pair of hydraulic pump motors having an input shaft and an output shaft communicating with each other and at least one of which has a variable displacement.
a differential gear and a second differential gear, drivingly coupling one of the pair of hydraulic pump/motor and a first element of the first differential gear to the input shaft; interlocking a first element of a two-differential gear device with the input shaft;
The other of the pair of hydraulic pump/motors is connected to the first hydraulic pump/motor.
drivingly coupled to a third element of the differential gear unit to interlock a second element of the first differential gear unit and a second element of the second differential gear unit, the second differential gear unit; a third element is interlocked with the output shaft, and a first disconnection means capable of arbitrarily disconnecting and disconnecting the second element of the second differential gear and the output shaft; and a first element of the second differential gear. and the input shaft, a second element of the second differential gear and a second element of the first differential gear
and a second interlocking means capable of arbitrarily releasing or connecting at least one of the interlocking with the third element of the second differential and the third element of the second differential and the output shaft. This is an output split type mechanical-hydraulic transmission with multiple speed ranges.

Embodiments of the present invention will be described below with reference to the drawings.

First, to explain the first embodiment, as shown in FIG. 1, 1 on the left is an input shaft, and 2 on the right is an output shaft.
are placed concentrically.

The numeral 3 below the input shaft 1 is a variable displacement type i-th hydraulic pump/motor, and the numeral 4 above the input shaft 1 is a fixed displacement second hydraulic pump/motor.

The rotating shafts 3a and 4a of both hydraulic pump motors are arranged parallel to the input shaft 1, and the rotating shaft 3a is connected to the input shaft 1 by a pair of gears 7 and 8.

Further, these two hydraulic pump/motors are hydraulically connected through oil passages 5, 6, and the volume D1 of the first hydraulic pump/motor 3 can be changed within a range from D1max to -D1max. 1-D1maxl
is equal to the volume of the second hydraulic pump motor 4.

The first differential gear device 9 on the right side of the input shaft 1 is Sangya S.

, Sangya S', Lingya R1, Sangya. Pinion P that meshes with Ya So % This pinion P.

It is formed by a planetary gear consisting of a long pinion P1 that meshes with sangya S1 and ring gear R1, and a carrier c1 that supports pinion Po and long pinion P1, and carrier C1 (first element) is integrally connected to input shaft 1. The sangya So (third element) is connected to the rotating shaft 4a of the second hydraulic pump/motor 4 through a set of gears 10.11.

The speed reduction device 12 on the right side of the first differential gear device 9 includes a sangya S2 integrally connected to the carrier C0 of the first differential gear device 9, a ring gear R2 fixed to the case 13, and a ring gear R2 and the sangya S2. Pinion P meshed with
2 and a carrier C2 that supports this pinion.

The second differential gear device 14 on the right side of this speed reduction device 12 is formed by a planetary gear consisting of a sun gear S3, a ring gear R3, a pinion P3 that meshes with the ring gear R3 and the sun gear S3, and a carrier C3 that supports this pinion. The carrier C3 (first element) is integrally connected with the carrier C2 of the reduction gear device 12, and the sangya S3 (second element) is connected to the ring gear R of the first differential gear device 9.
1 (second element).

The reversing device 15 on the right side of the second differential gear device 14 includes a sun gear S4 integrally connected to the ring gear R3 (third element) of the second differential gear device 14, a pinion P4 that meshes with this sun gear, and a pinion P4 that meshes with this pinion. pinion P'4,
The ring gear R4 can be arbitrarily connected to the case 13 with a planetary gear consisting of a ring gear R4 that meshes with this pinion P'4 and a carrier C4 that supports both pinions P4 and P'4 and is integrally connected to the output shaft 2. Brake B
It is formed by.

The outer periphery of this reversing device 15 includes a ring gear R4 and an output shaft 2.
A first clante CL, which can be arbitrarily connected to the
On the right side of the reversing device 15, a second clamper CL2, which can arbitrarily connect the sangya S3 and the output shaft 2, and a third clamper CL3, which can arbitrarily connect the sangya S1 and the output shaft 2, are arranged.

Incidentally, the hydraulic pump motors 3 and 4 are of axial piston type.

Further, as the brakes B1 and CL1, CL2, and CL3, friction type brakes that are engaged by hydraulic pressure are used.

Furthermore, the ratio of the pinte circle diameters of Sanghya and Lingya is R1/
S1= R2/ S2= R3/S3= R4/? 4
-2/1, R1/Soζ3/1, and the pinte circle diameter ratio of gear 8 to gear 7 is equal to the pinte circle diameter ratio of gear 11 to gear 10.

Thus, the first element [carrier C] of the second differential gear device 14
3] and the input shaft 1 is a driving connection via the reduction gear device 12, and the second element [ring gear R1] of the first differential gear device 9 and the second element [ring gear R1] of the second differential gear device 14 Interlocking with the element [Sangya S3] is an integral connection, and the second disconnection means is connected to the third element [Ring gear R3] of the second differential gear device 14.
) and the output shaft 2 can be arbitrarily released and connected, and at least the first clamp CL1 serves as the second disconnection means.

Next, the operation will be explained, but for convenience of explanation, it is assumed that the input shaft 10 rotational speed is constant and that there is no oil leakage between the two hydraulic pumps and motors 3 and 4.

When the first crank CL1 is engaged, the reversing device 15 becomes in the long position, the ring gear R3 and the output shaft 2 are integrally connected, and the first forward speed range is completed.

In this speed range, the first hydraulic pump motor 3
If the volume D1 is set to D1max, the second hydraulic pump/motor 4 will rotate at the same speed as the first hydraulic pump/motor 3,
As a result, Sanghya So becomes carrier C1 and Sanghya S2.
As a result, ring gear R3 and sangya S3 also rotate at the same speed as carrier C, etc., but since carrier C3 rotates at 1/3 the speed of carrier C0, etc., ring gear R3 and output shaft 2 rotate at the same speed as carrier C0, etc. Does not rotate, speed ratio e
is zero.

The volume D1 of the first hydraulic pump/motor 3 is set as shown in the second diagram.
When changing continuously from D1max to -D1max,
The rotational speed of the second hydraulic pump/motor 4 changes continuously, and the Sangya S.

As shown in the third diagram, the rotational speed of the rotational speed decreases continuously, reaches zero, and then continues to increase in the opposite direction.

As a result, the rotational speeds of the ring gear R1 and the sun gear S3 are continuously decreased as shown in the third diagram, and the rotational speeds of the ring gear R3 and the output shaft 20 are continuously increased as shown in the third diagram.
The speed ratio e increases continuously.

In this first forward speed range, by changing the volume of the first hydraulic pump/motor 3, the speed ratio e can be changed steplessly in the range of zero to 1/3. can be done.

If you want to further increase the speed ratio e, use the second Clante CL.
The first forward speed range is switched from the first forward speed range to the second forward speed range by engaging the second forward speed range and disengaging the first forward speed range CL.

At the time of this switching, the ring gear R3, the ring gear R, and the sangya S3 are exactly synchronized as shown in the third diagram.

Further, by bringing the ring gear R4 into a free state, the connection between the ring gear R3 and the output shaft 2 is released.

After that, when the volume D1 of the first hydraulic pump/motor 3 is continuously changed from <1 D1max to D1max as shown in the second diagram, the rotational speed of the second hydraulic pump/motor 4 continuously decreases to zero. After that, it continues to rise in the opposite direction, and the rotational speed of Sanghya So decreases continuously as shown in the third diagram.
After reaching zero, it continues to rise in the opposite direction.

As a result, the rotational speed of the ring gear R1 increases continuously as shown in the third diagram, and the speed ratio e continuously increases.

In this second forward speed range, by changing the volume of the first hydraulic pump/motor 3, the speed ratio e can be changed steplessly in the range of 1/3 to 1.0.

If you want to further increase the speed ratio e, use the third clante CL3.
The second forward speed range is switched to the third forward speed range by engaging the second clutch CL2 and disengaging the second clutch CL2.

At the time of this switching, the ring gear R1 and the sangya S1 are exactly synchronized as shown in the third diagram.

゛ After that, when the volume of the first hydraulic pump/motor 3 is continuously changed from <D1max to -D1max as shown in the second diagram, the rotational speed of the second hydraulic pump/motor 4 continuously decreases and becomes zero. After that, it continued to rise in the opposite direction and reached Sanghya S.

As shown in the third diagram, the rotational speed of the rotational speed decreases continuously, reaches zero, and then continues to increase in the opposite direction.

As a result, the Sangya S00 rotational speed increases continuously as shown in the third diagram, and the speed ratio e continuously increases.

Therefore, in this third forward speed range, by changing the volume of the first hydraulic pump/motor 3, the speed ratio e can be changed steplessly in the range of 1.0 to 5/2.

If the above operation is performed in reverse, the speed ratio e will be steplessly reduced from 5/2 to zero.

If you want to further reduce the speed ratio e from zero, that is, if you want to go backwards, engage the brake B and press the first clamper CL.
, and switches from the first forward speed range to the reverse speed range.

At the time of this switching, the ring gear R4 is just stopped as shown in the third diagram.

After that, when the volume of the first hydraulic pump 1/motor 3 is continuously changed from <Dlmax to -D1max as shown in the second diagram, the rotational speed of the second hydraulic pump/motor 4 continuously decreases and becomes zero. After that, it continues to rise in the opposite direction, and the rotational speed of the Sanghya So decreases continuously as shown in the third diagram, and after reaching zero, it continues to rise in the opposite direction.

As a result, the rotational speed of the ring gear R3 is continuously decreased as shown in the third diagram, the rotational speed of the carrier C4 is continuously decreased, and the speed ratio e is continuously decreased.

Therefore, in this reverse speed range, the first hydraulic pump
By changing the volume of the motor 3, the speed ratio e can be changed steplessly in the range of zero to -1/3.

The rotational speeds of pinions P0, P2, P3, and P4 are as shown in the fourth diagram.

In this first embodiment, switching between the first forward speed range and the second forward speed range is performed by connecting and disconnecting the sangya S3 and the output shaft 2 and the ring gear R3 and the output shaft 2. The disconnection between R3 and the output shaft 2 may be replaced by the disconnection between the carrier C3 and the input shaft 1 or the disconnection between the sangya S3 and the ring gear R1.

Next, a second embodiment will be described. In the fifth diagram, the input shaft 101 and the output shaft 102 are arranged concentrically.

Rotating shaft 1 of variable displacement first hydraulic pump/motor 103
03a is parallel to the input shaft 101, and a set of gears 107
, 108 are connected to the input shaft 101.

A fixed displacement second hydraulic pump/motor 104 is connected to the oil passage 10
5, 106 hydraulically communicates with the first hydraulic pump/motor 3, and its rotating shaft 104a is connected to the input shaft 10.
It is parallel to 1.

? 1 differential gear device 109 includes a sun gear S1, a pinion P that meshes with this sun gear, a pinion P/ that meshes with this pinion, and a ring gear R0 that meshes with this pinion P1.
and a planetary gear consisting of a carrier C0 that supports both pinions P and P1.

The carrier C (first element) is integrally connected to the input shaft 101, and the sangya Sl (third element) is connected to a set of gears 110.
, 111 to the rotating shaft 104a of the second hydraulic pump/motor 104.

The third differential gear device 11 on the right side of the first differential gear device 109
, 6 is a sangya S2, a pinion P2 that meshes with this sangya, an uppinion P6 that meshes with this pinion P2, a ring gear R that meshes with this pinion p4, and both pinions P.
2. It is formed by a planetary gear consisting of a carrier C2 supporting P6, and the ring gear R2 is the first
It is integrally connected to the carrier C1 of the differential gear device 109, and the carrier C2 is integrally connected to the ring gear R1 (second element) of the first differential gear device 109.

The speed reducer 112 includes a sun gear S3, a pinion P3 that meshes with this sun gear, and a ring gear R that meshes with this pinion.
The sun gear S3 is integrally connected to the carrier C0 of the first differential gear device 109.

The second differential gear device 114 includes a pinion P4 that meshes with the sun gear S, a ring gear R4 that meshes with this pinion, and a carrier C that supports the pinion P"4.
The carrier C4 (first element) is integrally connected with the carrier C3, and the planetary gear S4 (second element) is formed by an intermediate shaft 1.
17, and its ring gear R4 (third element) is also integrally connected to the output shaft 102.

The intermediate shaft 117 can be connected to the sangya S2 by the first clante CL, can be connected to the ring gear R1 and the carrier C2 by the second clante CL2, and can be connected to the output shaft 102 by the third clante CL3.

Brake B can connect ring gear R3 to case 113.

In addition, the pinte circle diameter of Sanghya and Lingya is R1/81=
3/1, R2/S2=R3/S3=R4/S422/
1, and the pinte circle diameter ratio of the gear 10B to the gear 107 and the pinte circle diameter ratio of the gear 111 to the gear 110 are the same.

Therefore, the interlocking between the first element [carrier C4] of the second differential gear device 114 and the input shaft 101 is a driving connection via the reduction gear device 112, and the first element [carrier C4] of the second differential gear device The interlocking of the three elements [ring gear R4] and the output shaft 102 is an integral connection, and the second disconnecting means is the second differential gear device 1.
14 first element [carrier C4] and the input shaft 101, and the second element [ring gear R0] of the first differential gear device 109 and the second element [sangya S4] of the second differential gear device 114. The interlocking of the brakes B1 and CL2 can be arbitrarily released and connected, and at least the brakes B1 and CL2 serve as the second disconnection means.

In the second embodiment configured as described above, the backward speed range is completed by engaging the first clutch CL1 and brake B, and the first forward speed range is completed by engaging the second clutch CL2 and brake B. 2nd clutch C
When L2 and third clutch CL3 are engaged, the second forward speed range is completed, and when first clutch CL and third clutch CL3 are engaged, the third forward speed range is completed.

In each of these speed ranges, the first hydraulic pump
If the volume D1 of the motor 103 is changed as shown in the sixth diagram, the members S1, R1, P1, Pi, S2, C2, P2,
The rotational speeds of P4, C3, R3, P3, S4, C4, R4, and P4 change as shown in Figure 7.8, and the speed ratio e changes.

Therefore, in this second embodiment, the speed ratio e is set to 1/3 to 5/3.
It can be changed steplessly within the range.

In this second embodiment, regarding switching between the first speed range and the second speed range, the disconnection between the carrier C4 and the input shaft is replaced by the disconnection between the ring gear R4 and the output shaft or the disconnection between the sangya S4 and the intermediate shaft. can do.

Next, a third embodiment will be described.

In FIG. 1, an input shaft 201 and an output shaft 202 are arranged concentrically.

Rotating shaft 2 of variable displacement first hydraulic pump/motor 203
03a is parallel to the input shaft 201, and -? Gya 207
, 208 are connected to the input shaft 201.

A fixed displacement second hydraulic pump/motor 204 is connected to the oil passage 20
5, 206 hydraulically communicates with the first hydraulic pump/motor 203, and its rotating shaft 204a is parallel to the input shaft 201.

The first differential gear device 209 includes a sun gear S1, a pinion P l that meshes with this sun gear, a ring gear R1 that meshes with this pinion, and a carrier C that supports the pinion P1.
The planetary gear S1 (third element) is formed by a planetary gear consisting of 0, and the planetary gear S1 (third element) is
It is connected to a rotating shaft 204a of a hydraulic pump/motor 204.

The third differential gear device 21 on the right side of the first differential gear device 209
6 is sangya S2, pinion P that meshes with this sangya
2. It is formed by a planetary gear consisting of a ring gear R2 that meshes with this pinion and a carrier C2 that supports the pinion P2, and the carrier C2 is connected to the input shaft 2.
01 and is integrally connected with the ring gear R1 (first element) of the first differential gear device, and its sangya S2 is integrally connected with the sangya S1.

The second differential gear device 214 is formed by a planetary gear consisting of a sun gear S3, a pinion P3 that meshes with this sun gear, a ring gear R3 that meshes with this pinion, and a carrier C3 that supports the pinion P3, and the carrier C3 (first element) The rotating shaft 203a of the first hydraulic pump/motor 203 is connected by a set of gears 218 and 219.
The sangya S3 (second element) is integrally connected to the intermediate shaft 217.

This intermediate shaft 217 can be connected to the ring gear R2 (second element) of the third differential gear device by the first clante CL1,
Further, it can be connected to the carrier C (second element) of the first differential gear device by the second clante CL2, and furthermore, the third clante C
It can be connected to the output shaft 202 by L3.

The fourth clante CL4 is the ring gear R of the second differential gear device.
3 (third ice requirement) and the output shaft 202 can be connected intermittently.

・In addition, the pinte circle diameter ratio of Lingya to Sanghya is R
1/S0-R2/S2=R3/S3-2/1, and the pin of gear 208 relative to gear 207? Circle diameter ratio and gap 21
The pinte circle diameter ratio of gear 211 to gear 0 and the pinte circle diameter ratio of gear 219 to gear 218 are the same.

Therefore, the interlocking between the first element [carrier C3] of the second differential gear device 214 and the input shaft 201 is a constant driving connection [gears 207, 208, rotating shaft 203a, gears 219, 21
8], and the second disconnecting means is an interlocking mechanism between the second element [carrier C2] of the first differential gear device 209 and the second element [sangya S3] of the second differential gear device 214, and
The third element of the second differential gear device 214 [ring gear R3]
The interlock between the output shaft 202 and the output shaft 202 can be arbitrarily released and connected, and at least the clamps CL2 and CL4 serve as the second disconnection means.

In the third embodiment configured as above, the backward speed range is completed by engaging the first crank CL1 and the fourth crank CL4, and the forward speed range is completed by engaging the second crank CL2 and the fourth crank CL4. When the speed range is completed and the second clamper CL2 and third clamper CL3 are engaged, the second forward speed range is completed and the first clamper C
When L and the third clutch CL3 are engaged, the third forward speed range is completed.

In each of these speed ranges, if the volume D0 of the first hydraulic pump/motor is changed as shown in FIG.
C3, pinions P1 to P3 are the 11th. 12, the lotus degree ratio e changes as shown in FIG.

Thus, in this third embodiment, the speed ratio e can be changed steplessly in the range of -0.5 to 2.

As mentioned above, in the present invention, the first differential gear device used in the second speed range is also used in the first speed range, and the first and second differential gear devices are used in the first speed range. Therefore, the configuration of the second speed range can be made single, and the relative rotational speed of the constituent members can be kept low, vibration and noise sources during normal use are reduced, and durability is also improved.

Since there are fewer countershaft type reduction parts, there are fewer parts that generate radial loads, and the number of bearings for this purpose is reduced, making it possible to downsize the device.

[Brief explanation of drawings]

Fig. 1 is a schematic diagram showing the configuration of the first embodiment, and Fig. 2 is a schematic diagram showing the configuration of the first embodiment. A diagram showing the relationship between the volume D and the speed ratio e of the first hydraulic pump/motor, and Figures 3 and 4 are the relationships between the speed ratio e' and the speed ratio e of the sun gear, ring gear, carrier, and pinion with respect to the input shaft. FIG. FIG. 5 is a schematic diagram showing the configuration of the second embodiment, FIG. 6 is a diagram showing the relationship between the volume D0 of the first hydraulic pump/motor and the speed ratio e, and FIG. FIG. 3 is a diagram showing the relationship between the speed ratio e' and the speed ratio e of the ring gear, carrier, and pinion. FIG. 9 is a schematic diagram showing the configuration of the third embodiment, and FIG. 10 is a schematic diagram showing the configuration of the third embodiment.
A diagram showing the relationship between the volume D0 and the speed ratio e of the hydraulic pump/motor, 11th. FIG. 12 is a diagram showing the relationship between the speed ratio e' and the speed ratio e of the sun gear, ring gear, carrier, and pinion with respect to the input shaft. 1, 101, 201... Input shaft, 2, 10
2,202...Output shaft, 3,103,203.
...First hydraulic pump motor, 4,104,20
4...Second hydraulic pump motor, 5,105,2
05, 6, 106, 206... Oil road, 9, 10
9,209...First differential gear device, 14,11
4,214...Second differential gear device, B...
...Brake, CL1, CL2, CL3, CL4...
...Kurante.

Claims (1)

[Scope of Claims] 1. A human power shaft, an output shaft, a pair of hydraulic pump motors communicating with each other and at least one of which has a variable displacement, a first differential gear device, and a second differential gear device, one of the hydraulic pump/motor and a first element of the first differential gear set are drivingly coupled to the input shaft, and a first element of the second differential gear set is interlocked with the input shaft. , the other of the pair of hydraulic pump motors is drivingly coupled to a third element of the first differential, the second element of the first differential and the second differential A third element of the second differential gear device can be interlocked with a second element of the second differential gear device, and a third element of the second differential gear device can be interlocked with the output shaft, and the second element of the second differential gear device and the output shaft can be arbitrarily disconnected. a first disconnecting means; and the second disconnecting means.
interlocking between a first element of a differential and the input shaft; interlocking between a second element of the second differential and a second element of the first differential gear; and a third element of the second differential. An output split type machine having a plurality of speed ranges, characterized in that it is provided with a second disconnecting means capable of arbitrarily releasing and connecting at least one of the interlocking elements and the output shaft. Hydraulic transmission. 2. The interlocking between the first element of the second differential gear and the input shaft is a driving connection via a reduction gear, and the second element of the first differential gear and the second differential The interlocking with the second element of the gear device is an integral connection, and the second disconnection means can arbitrarily release and connect the third element of the second differential gear device with the output shaft. An output split type mechanical-hydraulic transmission having a plurality of speed ranges as claimed in claim 1. 3. The interlocking between the first element of the second differential gear and the input shaft is a driving connection via a reduction gear, and the interlock between the third element of the second differential gear and the output shaft is The interlocking is an integral connection, and the second disconnecting means is an interlocking unit between the first element of the second differential gear and the input shaft, and the second element of the first differential gear and the second Claim 1 (q) An output split type machine having a plurality of speed ranges - Hydraulic transmission, wherein the interlocking with the second element of the differential gear device can be arbitrarily released and connected. Device. 4. The interlocking between the first element of the second differential gear and the input shaft is a driving constant connection, and the second disconnecting means connects the second element of the first differential gear and the second differential. Interlocking with the second element of the dynamic gear device, and the third element of the second differential gear device
An output split type mechanical-hydraulic transmission having a plurality of speed ranges as claimed in claim 1, wherein the interlocking between the elements and the output shaft can be released and connected at will.