JPH02190670A - Hydraulic continuously variable shift control device - Google Patents

Abstract

PURPOSE:To perform the hydraulic continuously variable shift with no aid by another gear type shift transmission device by communicating oil paths of the plunger of the first rotary member and the plunger of the fixed member of a control system via pump ports provided on the second rotary member and the rotary member of the control system. CONSTITUTION:The first rotary member 10 of a drive system for the input or output, the second rotary member 16 of the drive system for the output or input coaxial with it, and the fixed member 26 of a control system arranged on the rotary axis are provided. The rotary member 21 of the control system which is coaxial and integrally rotatable with the member 10 and has an operating face obliquely controlled at a variable angle against the face perpendicular to the axis and guides the plunger 23 of the member 26 on the operating face are provided. Oil paths of the plunger 13 of the member 10 and the plunger 23 of the fixed member 26 of the control system are communicated via pump ports 34 and 35 provided on the members 16 and 21.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates primarily to a hydraulic continuously variable transmission control device for automobiles and the like.

(Prior art) As this type of hydraulic continuously variable transmission control device,
-966 The one published in the special gazette is known.

In this case, the plunger is driven by the rotation of the swash plate, and the pump performs the pumping function.The transmission device includes a motor with the same configuration connected to the pump in a closed circuit, and the reaction torque generated in the pump is transferred onto the driven shaft. It is equipped with another gear-type transmission device that restores power to the driven shaft in parallel.

(Problems to be Solved by the Invention) The above-mentioned hydraulic continuously variable transmission control device requires another gear-type transmission device, so the input and output shafts must be configured as two parallel shafts. 1 as in driving control
No consideration is given to direct drive, in which the human output shaft is driven at the same rotation rate, or opadravure, in which the rotation of the output shaft is higher than the rotation of the input shaft.

(Object of the Invention) The present invention has been made based on the above circumstances, and can realize hydraulic continuously variable speed without the aid of other gear-type speed change transmission devices. The present invention aims to provide a hydraulic continuously variable transmission control device that can perform output and speed change control, and can realize all controls such as forward/reverse rotation, deceleration, direct drive, and overdrive.

(Means for Solving the Problems) Therefore, in the present invention, a first rotating member of an input or output drive system in which a large number of plungers are arranged around a rotational axis, and a first rotating member coaxial with the first rotating member are provided. The plunger is configured such that the entire plunger is guided in an operating plane inclined at a predetermined angle with respect to a plane perpendicular to the axis of rotation. a second rotary member of the drive system for output or input, a fixed member of the control system in which a number of plungers are arranged around the rotation axis, and a first rotary member of the control system.
An operating surface that is coaxial with and rotatable integrally with the rotating member, and whose tilting is controlled at a variable angle with respect to a plane perpendicular to the axis? and configured to guide a plunger in a fixed member of the control system in this operating surface.1. (a pump port provided on the second rotating member and the rotating member of the control system)? The oil passages of the plunger of the first rotating member and the plunger of the fixed member of the control system are communicated through the oil passage.

(Function) Therefore, structurally, all the constituent elements are arranged on one axis, so the overall structure can be made compact, and since no separate transmission device such as a gear type is used, the structure is also simple. Moreover, the reaction torque caused by the pump operation is also recovered to the output side, and the area of gear change control in particular covers all controls such as forward/reverse, deceleration, direct drive, and overdrive, making it ideal for vehicles such as automobiles. Can be used in advanced control systems.

(Example) Hereinafter, an example of the present invention will be specifically described with reference to the drawings.

In the figure, reference numerals 1 and 2 are frames of the speed change control device, which pivotally support a rotating shaft 5 via bearings 3 and 4f. The rotating shaft 5 has a sleeve 6 that directly receives the bearing 3 fixed by a nut 7 screwed onto the rotating shaft 5, and also directly supports the bearing 4, so that the inner ring of the bearing 4 is fixed. The sleeve 8 is fitted into the sleeve 8 with the nut 9 screwed onto the rotating shaft 5. It is configured to be fixed.

The rotary shaft 5 has a first drive system for output or input.
The rotating member IO is integrally constructed.

The rotating member 10 has a large number of cylinder holes 12 arranged in a predetermined pitch circle around the rotation axis, and a plunger 13 is slidably fitted into the cylinder holes 12. If necessary, the plunger 13 and the cylinder hole 12
It is best to keep it as oil sealed as possible. Each of the cylinder holes 12 has a passage 14 extending in the radial direction.
The openings 15 are arranged in a pitch circle having a smaller diameter than the pitch circle described above and are connected to the entrance/exit 15 formed in the rotating member 10 through the opening 15.

A second rotating member 16 of a drive system for input or output is rotatably supported on the rotating shaft 5 via a bearing 1lvi. The second rotating member 16 has an operating surface 178 that is coaxial with the first rotating member 1O and inclined at a predetermined angle with respect to a plane perpendicular to the rotational axis. The plunger 13 is rotatably supported by an operating body 171 via a Ni-last bearing 18, and the outer end of the plunger 13 is in contact with the operating surface 17a. The second rotating member 16 also has half-arc-shaped pump boats 19 and 2 divided on the left and right in the direction of inclination of the operating surface 17a, corresponding to the above-mentioned entrance/exit 15.
0.

Furthermore, a control system rotating member 21 is integrally formed on the rotating shaft 5 together with the first rotating member 10 . The rotating member 21 is coaxial with the first rotating member 10 and can rotate integrally therewith.

Further, the frame 2 is provided with a structure surrounding the rotating shaft 5.
A control system fixing member 26 is provided within the unit, and this fixing member 26 has a large number of cylinder holes 22 arranged in a predetermined pitch circle around the rotation axis, similar to the first rotating member 10 described above. is bored, and this has a plunger 23
are slidably fitted. However, if necessary, it is preferable that the plunger 23 and the cylinder hole 22 be in an oil-sealed state as much as possible. Each of the cylinder holes 22 communicates with an inlet/outlet 25 formed in the fixing member 26 through passages 24 extending in the radial direction, while being arranged on a pitch circle having a smaller diameter than the pitch circle described above.

On the other hand, the above-mentioned rotating member 21 has an operating surface 27a k whose tilting is controlled at a variable angle with respect to a plane orthogonal to the rotational axis.
The actuating body 27 is provided with an actuating body 27 having a The actuating body 27 is rotatably supported by a control member 29 via a thrust bearing 28, and the control member 29 is connected to the actuating surface 27a.
The rotating member 2 is tiltable about a pivot shaft 30 centered at the top.
It is pivoted to 1. Further, a control element 31b having a ball 31a is attached to the control member 29, and a bearing 31 is provided between the control element 31bt, and the control element 31b is controlled so as to move in parallel while being sandwiched between the forks 32. A rod 33 is connected to a controller* (not shown) on the frame 2 side. The plunger 23 is in contact with the operating surface 27a.

Further, the rotating member 21 is provided with half-arc-shaped pump boats 34 and 35 that are divided on the left and right sides in the direction of inclination of the operating surface 27a, corresponding to the above-mentioned entrance and exit port 25.

The pump boat 34 is communicated with an oil passage 38 provided on the rotating shaft 5, and the pump boat 35 is communicated with an oil passage 39. On the other hand, the pump boat 19.20 is also connected to
The annular passages 36 and 37 are respectively connected to the annular passages 36 and 37 provided in the rotating shaft 5 through the through holes t9a and 20at, and the annular passages 36 and 37 are each communicated with the oil passages 38 and 39, respectively.

Further, control hydraulic pressure is supplied to the oil passages 38 and 39 from a hydraulic pump 44 via check valves 40 and 41 and passages 42 and 43, respectively.

The hydraulic pump 44 communicates with its suction side noise oil tank 45, and its delivery side communicates with the oil tank 45, bypassing the pressure regulating valve 46. The control pressure of this pressure regulating valve 46 can be adjusted by a control system 47. Note that the above-mentioned rotating member 1
Oil leaking from the joint surface between the inlet/outlet 15 of the rotary member 16 and the pump boats 19 and 20 of the rotary member 16 and the sliding part between the cylinder hole 12 and the plunger 13 leaks to the outside of the oil pan 4Flt. - is collected in the oil tank 45 through the oil tank 45. In addition, the above-mentioned fixing member 26
Oil leaked from the joint surface between the inlet/outlet 25 and the pump boats 34 and 35 of the rotating member 21 and from the sliding part between the cylinder hole 22 and the plunger 23 also leaks to the outside. Similarly to the above, the oil pan 4
8 and is collected in the oil tank 45.

In the figure, reference numeral 49 is an output or input gear provided on the first rotating member 10, and 50 is an input or output gear provided on the second rotating member 16.

In such a configuration, while the cylinder hole lλ22 and each hydraulic path connected thereto are filled with oil,
For example, when power is transmitted to the second rotating member 16 via the gear unit 50 and the hydraulic pump 44 is driven, the oil in the hydraulic path is maintained at the pressure value set by the pressure regulating valve 46. , when the second rotating member 16 rotates at the speed R, the first
The rotating member 10 is rotated at a speed of ``.Thereby, torque is transmitted from the second rotating member 16 to the first rotating member 10 via the gear portion 49 at a gear ratio a = ``/''. The point of generating such a gear ratio will be described in detail below.

Now, we will consider the pump discharge area QAt due to the respective speeds R and r between the second rotating member 16 and the first rotating member io and the first rotating member IO. When the first rotating member 10 does not rotate, that is, when r = Q, the second rotating member 1
6 rotates clockwise in FIG.
is pressed and pump discharge amount QA=Q? At the same time, on the pump boat 20 side, there is a plunger! 3 is the operating surface 17a
Following K, the pump suction amount QB=Qt- is obtained. If the first
Assuming that the rotating member 10 is rotated at a speed r in the same direction as the second rotating member 16, the relative speed of both rotating members 16 and lO is (r), and the discharge amount QA on the pump boat 19 side is −r QA=()Q ・Old...(1) −π− Similarly, the suction amount QB on the pump boat 20 side is −r QB=(−π−)Q ・・・・・・(2) On the other hand, If the first rotating member 10 rotates at a speed r, the rotating member 21 of the control system rotates together with it, so the speed is r. Therefore, the operating surface 27aK of the rotating member 21, the plunger 23 follows, and the pump suction amount QA'? At the same time, if the plunger 23 is pushed by the operating surface 27a and the pump discharge amount Q33/l is obtained on the pump boat 35 side, then the rotating member 2
Pump flow rate Q' when 1 rotates at speed R = k Q
Then, the pump suction amount QA' and the pump discharge amount' at the speed r are respectively QB'=π・kQ (4) In this case, k is the difference between the second rotating member 16 and the rotating member 21. is the ratio (coefficient) of the discharge amount Q' determined by the inclination angle of the operating surface 27a to the discharge amount Q determined by the inclination angle of the operating surface 17a when the rotational speed is the same.

From this, when the second rotating member 16 rotates at a speed r, the first rotating member 10 rotates at a speed r, K is Q A between the pump boats 19 and 34 and the pump ports 20 and 35 due to pumping. An oil flow of = Q A/ and Q B = Q B/ must be achieved via the oil channels 38 and 39.

From equations (1) and (3), 几-r QA=(-D-)・Q=QA'=(R)・k-QQ B
= (7)・Q=QB′=(i)・k−Q From the above formula
k=(R-r)/r (5) Now, the actuating body 27 is tilted by the operation of the control rod 33 at an inclination angle α of its actuating surface 27a as shown in FIG. hour, 1
(If ==l, then k = 1 = ()L-r)/r Therefore, r=L/2 When the second rotating member 16 rotates at a speed R, the first rotating member 1O rotates at a speed R/2. I will do it.

Also, when the actuating body 27 makes the inclination angle α=O of the actuating surface 27a t'' by operating the control rod 33, as shown in FIG. , the second rotating member 16 and the first rotating member lO are in a coupled state, and a direct transmission is achieved. This shows the case where =0.

Similarly, if 0<k<1, then the relationship is rFiu>r>u/2o.

If k)l, that is, Q/>Q, in this embodiment, when the slope angle α' of the slope 17a and the slope α>α' of the slope 27a, r(R/2 becomes.

Incidentally, if Q''-2Q, then in Jin's example, sin α = s
in2α′), r=R/3.

When you want to expect overdrive, it is necessary to set k(O. In other words, the inclination angle α of the operating surface 27a is the rotation axis S
Angle a! with a negative sign beyond the plane orthogonal to ’ to take K
Become.

In the above embodiment, the gear section 49 may be used as an input section, and the gear 50 may be used as an output section. In this case, pump ports 20 and 34 are on the discharge side, and pump ports 19 and 35 are on the suction side (assuming the same direction of rotation as in the previous embodiment). Further, the tilt angle of the tilt body 27 is on the negative side. That is, when the first rotating member 10 rotates at a speed "R" and the second rotating member 16 rotates at a degree of rotation "r", the suction amount QB=(-π-)Q from the discharge ratio -r)19 from the pump port 20. is obtained.

- At this time, when the rotating member 21 of the control system is rotated at a speed of 1, suction tQA'=kQ can be obtained at the pump port 34, while discharge amount QB'=Qk can be obtained at the pump port 35.

Q A = Q A/and Q B = Q B/From the above formula, k = (R-r)/R This means that 1 (when = l, that is, when Q' = Q, the second
Even if the first rotating member 10 rotates at a speed R, the rotating member 16 is not driven at r=0.

Also, when k=0, that is, QA=QA'=o, QB=
QB'=of)tpKFi, the 100E member 10 and the second rotating member 16 are in a coupled state, and r=r.

If O<k<1, then r〉r〉0　.

- If you want to expect overdrive, it is necessary to set k<O. Furthermore, if you want to expect a reversal, it is necessary to set k>1.

In the above embodiment, reference numeral 51 indicates a thrust bearing provided between the frame 1 and the second rotating member 16, and reference numeral 52 indicates a thrust bearing provided between the frame 2 and the sleeve 8.

Further, in the above embodiment, the operating surface 17a or the operating surface 27
Although the configuration has been described in which the plungers 13 and 23 are only in contact with the K, it is also possible to use a configuration in which each plunger 13 or 23 is pivotally connected to the actuating body I7 or 27 using a link. Of course. The operating surfaces 17a, 27a referred to here mean functional slopes that guide the plunger 13, 23f to perform the pumping action, and are not structurally restricted.

In addition, in this embodiment, the actuating surfaces 17a, 278'Ik
The actuating body 17.27 is formed respectively on the actuating body 17.27.
27t-Although it is rotatably supported by the second rotating member 16 and the control member 29, it goes without saying that it may be formed directly on the second rotating member 16 and the control member 29.

Further, although the hydraulic pressure is supplied from the hydraulic pump 44 via the rotating shaft SQ, it goes without saying that the hydraulic pressure may be supplied from any other suitable location.

(Effects of the Invention) The present invention has been described in detail above, and a hydraulic continuously variable speed can be realized without the aid of other gear type speed change transmission devices. 1. Alternatively, the first rotating member of the drive system, the second rotating member of the coaxial core, the rotating member of the control system that is integrated with the first rotating member, and the fixed member are arranged coaxially. The swash plate pump structure and the variable swash plate pump structure constructed between the pump and the swash plate pump structure realize stepless speed change, and are highly efficient speed change control devices that can recover reaction torque generated in the pump to the driven member. .

In addition, if the input and output are taken into consideration, the speed change range can be selected to suit the application, and control such as forward/reverse, deceleration, and direct drive overdrive can be realized.

[Brief explanation of the drawing]

Fig. 1 is a vertical side view showing an embodiment of the present invention, Figs. 2 to 5 are cross-sectional views taken along lines -1 to V-V in Fig. 1, and the sixth factor is control operation. FIG. 7 is a longitudinal side view for explaining the control member, and FIG. 7 is a front view of the control member. 10...First rotating member Work 2...Cylinder hole 13
...Plunger 15...Entrance/exit 16...Second
Rotating member 17... Operating body 21... Rotating member (control system) 22... Cylinder hole 23... Plunger 25... Inlet/outlet 26... Fixed member 27.
... Actuation body 27a ... Actuation surface 29 ... Control member 34.35 ... Pump port

Claims (1)

[Claims] A first rotating member of an input or output drive system in which a large number of plungers are arranged around the rotational axis, and a rotating member that is coaxial with the first rotating member and inclined at a predetermined angle with respect to a plane perpendicular to the rotational axis. a second rotary member of the drive system for output or input configured to guide the plunger on the operating surface thereof; a fixed member of the control system in which a number of plungers are arranged around the rotational axis; It has an operating surface that is coaxial with the member and can be rotated integrally therewith, and whose tilting is controlled at a variable angle with respect to a plane perpendicular to the axis, and on this operating surface, the plunger of the fixed member of the control system is rotated. and a rotating member of the control system configured to guide the plunger of the first rotating member and the fixed member of the control system through pump ports provided in the second rotating member and the rotating member of the control system. A hydraulic continuously variable transmission control device, characterized in that an oil path of a plunger is communicated with each other.