JP2002250411A - Fluid control variable speed change gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid control variable speed change gear which is small in setting space and simple in structure. SOLUTION: A plural set of planetary gear mechanisms having different sizes are coaxially stored in a rotatable gear housing, the flow of working fluid made to flow by the input rotation generated at a gear engagement part is controlled, to change the relative rotation between planetary mechanisms to attain a variable speed output rotation.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission in a power transmission device for general industrial machines, construction machines, and automobiles.

[0002]

2. Description of the Related Art A continuously variable transmission combining a conventional planetary gear mechanism and a fluid rotary machine, for example, a planetary gear having three reduction ratios of a sun gear, a planetary gear, and an internal gear corresponding to respective reduction ratios. A mechanism used in automobiles and the like, in which a mechanism is arranged in several stages, and each internal gear is braked by a brake mechanism or the like to change the speed with a torque converter interposed, and a planetary gear mechanism There is a transmission that obtains a continuously variable transmission by applying a rotation change from a hydraulic pump to two gear elements.

[0003]

A conventional planetary gear mechanism and a continuously variable transmission composed of a fluid rotating machine have a large number of components and are complicated. Therefore, simplification reduces the number of parts and the installation space.

[0004]

In order to achieve the above object, the gear mechanism is a simple planetary gear mechanism comprising only a sun gear and a planetary gear, and the gear mechanism is filled with hydraulic fluid. The input rotation by one of the gear elements gives relative rotation between the planetary gear and the sun gear in proportion to the resistance of the hydraulic fluid, and the planetary gear rotates and revolves.

[0005] The rotation of the planetary gear imparts a discharging force to the hydraulic fluid before and after the gear meshing portion with the sun gear, and generates a suction force on the opposite side. By controlling the flow of the hydraulic fluid discharged, the rotation of the planetary gears receives the drag and changes.The planetary gears rotate in the input rotation according to the ratio of the drag, and the planetary gears rotate the sun gear. The change of the distribution to the revolution is taken as the output rotation.

For example, as shown in FIG. 7 in the first embodiment, a sun gear integrated with an output shaft is opposed to a sun gear integrated with an output shaft on the same axis of a flange portion integrated with an input shaft. In a structure in which the gears are housed in the gear housing of the flange, filled with hydraulic fluid, and sealed with a ring-shaped gear housing lid, the planetary gear for input rotation revolves on the sun gear, but the gear meshes The flow caused by the discharge of the hydraulic fluid generated in the part, by the resistance of the control valve installed in the path, gives a resistance to the rotation to the gear meshing part, causing the sun gear to generate rotation changed according to the resistance, and output rotation And

In the case where the input rotation is the revolution of the planetary gear and the sun gear is the output rotation, in a state where the flow of the filled hydraulic fluid is sealed by the control valve, the planetary gear is driven by the drag of the meshing portion of the gear. The revolution given to the planetary gear, which cannot rotate on the sun gear, becomes the rotational force of the sun gear as it is.

Conversely, if the control valve is fully opened to allow the hydraulic fluid to flow freely, assuming that there is no fluid, no mechanical resistance, etc., the planetary gear is driven by the hydraulic fluid from its gear meshing part. Because it does not receive drag, the orbit given freely to the planetary gear by rotating freely on the sun gear is not transmitted to the sun gear and the output shaft does not rotate.

Accordingly, when the flow of the hydraulic fluid is gradually reduced and the drag of the gear meshing portion is increased, the rotation of the planetary gear from the input shaft is gradually converted to the revolution, and the output rotation of the sun gear corresponding to the rotation is gradually increased. Will be done.

[0010] Since the discharge and inflow of the hydraulic fluid of the gears occur before and after the meshing portion between the adjacent planetary gears, the hydraulic fluid flows through the portion through the conduction hole, and the flow rate of the hydraulic fluid in the path. Install control valves for control purposes.

A transmission in which the control valve is housed in a gear housing and a transmission in which the control device is separated from the transmission and separately installed are conceivable, and a transmission that meets the installation conditions and operating conditions is realized. I can do it. In the first and third embodiments, the control valve is housed in the transmission, and in the second and fourth embodiments, the control valve is omitted from the inside of the transmission.

The first embodiment has a mechanism capable of operating the opening of the control valve. There are several protrusions on the back of the flange, which are fitted to the holes provided in the control disk so as to be movable in the axial direction, and the control disk obtains the force to rotate integrally from the protrusions of this flange. I have. The valve stem of the control valve that penetrates from the back of the flange is joined to the control disk at the shaft end and has a structure that interlocks with the movement in the axial direction.

The central portion of the control disk fits into the U-shaped groove of the screw wheel and slides and rotates, but the axial movement is restricted by the screw wheel.

The screw ring is combined with the outer surface of the input bearing protruding inside the main body casing by parallel screws.
When this screw wheel is rotated, it is configured to move in the axial direction according to the rotation. Therefore, the amount of rotation of the screw wheel is proportional to the amount of movement of the control valve in the valve axis direction via the control disk fitted into the U-shaped groove.

The screw wheel is assembled with an external gear wheel and an axially movable spline, and the external gear wheel meshes with the worm gear. The shaft of the worm gear is connected to a handle provided outside the main body casing, and by rotating this handle, the worm gear is rotated and the screw wheel is rotated via the external gear wheel. ing. Therefore, the control valve opening degree is changed by operating the handle to change the rotation of the output shaft.

The body casing is provided with screw plugs for filling and discharging the working fluid. The screw plug for filling is provided with a ventilation hole for avoiding expansion of the working fluid and air in the main casing due to a rise in temperature during operation. Further, a transparent window through which the state of the hydraulic fluid can be checked, a working hole at the time of assembling, and the like may be appropriately provided at necessary positions in the main body casing.

FIG. 11 shows the basic principle of the second embodiment. The second embodiment has a simplified structure without the control valve and its control mechanism of the transmission of the first embodiment. A gear meshing part that discharges hydraulic fluid at several places and a conduction hole that communicates with a gear meshing part that flows in the same number of hydraulic fluids pass through the input shaft, and are separated into two systems of discharge and inflow at the bearing part. It has a structure that leads to a connection port with the outside. The hydraulic fluid circulates through a control mechanism installed outside and the transmission through piping. By arranging the transmission and the control mechanism remotely, there are advantages that the installation conditions of the transmission, maintenance of the hydraulic fluid, and various control methods can be performed, and the application range is considered to be expanded.

In the third embodiment, two sets of planetary gear mechanisms having different sizes are arranged on the input side and the output side, respectively.
The sun gear rotating integrally with the output shaft is opposed via a gear housing, and the planetary gears are meshed with each other and housed in the housing. The revolution of the input and output planetary gears and the rotation of the gear housing are the same. By making the flow of the hydraulic fluid generated on the input side act on the planetary gear mechanism on the output side via the control valve, the transmission has a structure capable of transmitting a large amount of torque. FIG. 17 shows a basic principle in a bird's-eye view.

The flow due to the discharge of the hydraulic fluid generated at the meshing portion of the planetary gears on the input side receives resistance according to the ratio from a control valve whose valve opening changes in advance in proportion to the inflow pressure, and receives planetary gears according to the resistance. Cause a revolution. The hydraulic fluid that has passed through the control valve flows into a meshing portion that generates output rotation of the output-side sun gear. The planetary gear mechanism on the output side has a gear configuration that generates lower rotation and higher torque than the planetary gear mechanism on the input side. The rotational force generated by the hydraulic fluid that has passed through the control valve acting on the gear meshing portion on the output side and the revolving force of the planetary gear distributed by the resistance of one control valve are combined by the planetary gear mechanism on the output side. , Output rotation can be obtained.

In the two sets of planetary gear mechanisms having different configurations, for example, if the thickness of the gear in the axial direction is twice as large as that of the input side on the output side, ie, the displacement of the hydraulic fluid due to meshing of one set of gears is doubled. The number of revolutions on the output side is １ ／ of the number of revolutions 1 on the input side.

Further, at the rotation speed of the sun gear under the same conditions, the pressure of the hydraulic fluid generated at the meshing portion of the planetary gear is inversely proportional to the reference pitch circle diameter, and the discharge amount is proportional. Therefore, when the reference pitch circle diameter of the output side sun gear is twice as large as that of the input side, and the gear of the output side planetary gear mechanism is twice as thick as the input side planetary gear mechanism in axial direction, there are various cases. By ignoring the loss of rotation, the displacement volume difference due to the difference in tooth profile, etc., the approximate output rotation is 1/4 of the input rotation speed and the torque is 4 times. Therefore, various transmissions can be realized by combining planetary gear mechanisms having different sizes depending on the application.

When no load is applied to the output shaft, the input rotation is not enough to cause the pressure discharged from the hydraulic fluid to act on the control valve at the meshing portion of the input side planetary gear to act on the control valve, and the control valve is closed. And the working fluid in the gear housing does not flow. The input rotation is the same no-load rotation as the gear housing and the output shaft, and the reduction ratio is 1.

On the contrary, when the output shaft receives the maximum load,
The pressure at which the hydraulic fluid is discharged from the meshing portion of the input gears is maximized, and the control valve is fully opened. Therefore, all hydraulic fluid flows into the meshing part of the planetary gear on the output side,
The rotation of the output shaft becomes the maximum torque and the minimum rotation speed in the combination of the planetary gear mechanisms.

When the load on the output shaft gradually decreases, the pressure of the working fluid also decreases accordingly, and the opening of the control valve decreases proportionally. Therefore, the rotational force of the input shaft reduces the distribution of the reduction gear ratio generated at the meshing portion of the output side planetary gear to the rotation force having a large reduction ratio, and increases the distribution of the reduction ratio applied to the gear housing to the revolving force having a small reduction ratio. These respective rotational forces are gradually transmitted to the output shaft at a high rotation and a low torque.

The hydraulic fluid that has acted on the gear meshing portion via the control valve is carried to the meshing portion for discharging the next planetary gear with the rotation of the output-side sun gear, and is connected to the conduction hole provided on the gear housing wall. It passes through the hole and flows into the gear meshing portion having the suction function on the input side. The hydraulic fluid returns to the input side and circulates again.

It is desirable that the transmission of the force between the sun gear and the plurality of planetary gears meshing with the sun gear operate under uniform conditions. In the closed circuit in which the control valve is built in the gear housing, an annular communication hole is provided in each of the input and output gear housing lids, and the same working gear pressure is opened and communicated between the gear meshing gaps so that the pressure of the working fluid is uniform. The structure is such that the conditions are satisfied for each planetary gear mechanism.

Therefore, even if there are differences in pressure characteristics among a plurality of control valves, a uniform power transmission is realized between each planetary gear and the sun gear. Conversely, by changing the characteristics of the plurality of control valves by a spring or the like, a wide range of characteristics of the control valve can be obtained.

The hydraulic fluid in the spring chamber flows out and in according to the movement of the valve body of the control valve. The hydraulic fluid is guided to the gear meshing portion on the inflow side by grooves formed in the gear housing lid on the output side. ing.

Since the input and output planetary gears are both housed in an integral gear housing, the rotation of the gear housing and the revolution of the planetary gear are the same, and the rotation is determined by the input rotation and the load on the output shaft. Is done. The gear housing has a reverse rotation preventing device installed on the inner surface of the input side main body casing lid to prevent reverse rotation, and is assembled with the input side gear housing lid lid and splines.

The fourth embodiment has a structure on the assumption that the control valve built in the gear housing of the third embodiment is eliminated, and the control valve is separated from the transmission and externally operated. The discharge of the hydraulic fluid generated in the sun gear mechanism on the input side joins through the conduction holes in the input shaft and connects to the outside near the bearing of the input shaft. Similarly, the hydraulic fluid communication holes communicating with the pressure receiving portion of the sun gear mechanism on the output side also have a structure in which the respective communication holes merge in the input shaft in the input shaft and are connected to the outside via the shaft.

By performing the control of the hydraulic fluid externally, there is an advantage that maintenance such as heat radiation of the temperature rise of the hydraulic fluid accompanying the operation and replacement of the hydraulic fluid can be easily performed. Since the hydraulic fluid can be connected to a remote control device from the installation location of the transmission by the hydraulic fluid piping, the transmission can be realized according to various use conditions.

At the gear meshing portion in the planetary gear mechanism, a pressure difference occurs before and after that. Therefore, in order to minimize the leakage of the hydraulic fluid from the high pressure section to the low pressure section, the
It is possible to provide a gap between the two planetary gears so as to reduce the pressure difference and to form a structure in which the gaps where a large pressure difference occurs are separated. FIG. 10 shows an example of use according to the second embodiment. If there is no problem in arrangement, it is considered that such a structure of the planetary gear is effective against leakage.

The hydraulic fluid is subjected to pressure according to the load on the output shaft at the discharge portion of the meshing portion of the gear, so that the sliding portions such as the gear and the housing are manufactured precisely to prevent leakage of the hydraulic fluid. Therefore, it is desirable to appropriately install O-rings, oil seals, and the like.

In the case of a structure in which the control valve is housed in a gear housing to seal the working fluid, the working fluid may expand due to a rise in temperature due to operation. In Example 1, the valve was built in the control valve shaft, and in Example 3, it was installed on the gear housing lid.

[0035]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described based on Embodiments 1, 2, 3, and 4 with reference to the drawings. Example 1 is “Claim 1”, “Claim 2”, “Claim 4”, Example 2 is “Claim 1”, “Claim 5”, and Example 3 is “Claim 1”, "Claim 3"
"Claim 4" and Example 4 are respectively related to "Claim 1", "Claim 3", and "Claim 5".

[0036]

Embodiment 1 Embodiment 1 will be described with reference to the drawings.
1, 2, 5, and 6, a control valve 7 is mounted on a flange portion 1 a of an input shaft 1, and a planetary gear 3 and one of output shafts 2 are connected to a housing of a gear. The sun gear portion 2a is housed in the housing portion while being fitted to the bearing portion.

In FIG. 1, the flange portion 1a of the input shaft 1
Gears assembled in the cavity of the housing and
Fill the working hole with hydraulic fluid. The gear housing lid 4 is fixed to the flange portion 1a with screws 19 to seal the inside of the housing.

1 and 3, a worm gear retainer 13 is assembled on the inner wall of the main body casing 5 together with the external gear wheel 12 and the worm gear 14 and attached with screws 20. The screw ring 11 is mounted on the parallel screw part on the projection part 5a of the input shaft bearing, and is fitted and assembled with the spline part so as to be movable in the axial direction with the inner diameter of the external gear wheel 12. The shaft of the handle 15 is inserted from the upper part of the main body casing 5 and fitted to the worm gear shaft insertion joint 14a to assemble. The control disk 9 is fitted into the U-shaped groove of the screw wheel 11.

1, 3 and 6, the flange 1
The input shaft 1 of the rotating body integrated with a is fitted to the bearing of the main body casing 5, and the control disk 9 is fitted to the protrusion 1d of the flange 1a. A shaft end portion of the control valve 7 is fixed to the control disk 9 with a screw 10.

In FIG. 1, after assembling inside the main casing 5, the bearing of the main casing lid 6 is fitted to the output shaft 2, and the main casing 5 is fixedly sealed with screws 18. An appropriate amount of working fluid is filled from the working fluid filling port in the upper part of the casing, and the working fluid filling port is screwed with the screw plug 16.

Embodiment 2 Referring to FIGS. 8, 9, 10, and 11, the control valve incorporated in the flange portion 1a of Embodiment 1 is eliminated, and a gap 35b for discharging the hydraulic fluid meshed with the gear is provided. ,
Each of the conduction holes communicating with the gap 35c for the inflow of the hydraulic fluid is configured to open to a connection port outside the transmission main body via the flange portion 1a and the inside of the input shaft 1, and is similar to the first embodiment except for the control mechanism. Shall be.

FIG. 10 shows a pair of two planetary gears of the second embodiment for the purpose of reducing the leakage of hydraulic fluid before and after the gear meshing portion. Are shown below.

In the third embodiment, FIGS. 12, 13, 14,
16 and FIG.
Attach. A sun gear 42a of the output shaft 42;
The planetary gears 44 are incorporated in the respective housing portions of the gear housing 45, and the output-side gear housing lid 47 in which the abnormal pressure adjusting valve 59 is incorporated is attached with screws 64 and sealed.

12, 13, and 14, the input shaft 41 is inserted through the center of the gear housing 45 and fitted to the bearing of the output shaft 42. At the same time, the sun gear 41a is incorporated into the gear housing 45. The planetary gear 43 is incorporated into the gear housing 45, and the gear housing lid 46 is attached with the screw 63. It is preferable to assemble the inside of the gear housing by a working fluid bath operation and simultaneously fill the working fluid.

In FIGS. 12 and 13, a reverse rotation prevention device 51 is attached to the main body casing lid 49 with screws 60. The assembled input shaft 41, output shaft 42, gear housing 45, and input shaft 41 of the rotating body integrated with the gear housing lids 46 and 47 are inserted from the inside of the main body casing lid 49 on the input side, and simultaneously the gear housing Lid 46
The central projecting portion and the reverse rotation preventing device 51 are connected to the spline portion 46b.
Assemble at The bearing 53 is attached to the input shaft 41 and the housing of the main body casing lid 49, and the bearing retainer 55 is fixed with the screw 65.

Main casing 48 and main casing lid 4
9 is assembled with screws 61. Further, the main body casing lid 50 is assembled to the main body casing 48 with the screws 62.
The bearing 54 is mounted on the output shaft 42 and the housing of the output side main body casing lid 50, and the bearing retainer 56 is fixed with the screw 66. Other oil seals, O-rings, and the like are omitted as they are appropriately attached in each assembly process.

In the fourth embodiment, FIGS. 18, 19, and 2
In 1, the sun gear 82 a of the output shaft 82 and the planetary gear 84 are incorporated in each housing part of the gear housing 85, and the output gear housing cover 87 is attached with the screw 104.

In FIGS. 18, 19 and 20, the input shaft 81 passes through the center of the gear housing 85 and is fitted to the bearing of the output shaft 82. Sun gear 81a of input shaft 81
Are also stored in the gear housing 85 at the same time. Planetary gear 8
3 is incorporated into each housing of the gear casing 85, and the gear housing lid 86 is attached with screws 103.

In FIGS. 18 and 19, a reverse rotation prevention device 91 is attached to the main body casing lid 89 with screws 92. The assembled input shaft 81, output shaft 82, gear housing 85, gear housing cover 86, and input shaft 81 of the rotating body integrated with 87 are inserted from the inside of the input side main body casing cover 89, and simultaneously the gear housing cover The central projecting portion 86 and the reverse rotation prevention device 91 are assembled by the spline portion 86b.

The bearing 93 is mounted on the input shaft 81 and the housing of the main body casing cover 89 on the input side, and the bearing retainer 95 is fixed with screws 99. The main body casing 88 and the main body casing lid 89 are fixed with screws 101. The output side main body casing lid 90 is fixed to the main body casing 88 with screws 102. The bearing 94 is mounted on the output shaft 82 and the housing of the main body casing cover 90 on the output side, and the bearing retainer 96 is fixed with the screw 100. Other oil seals, O-rings, etc. shall be attached appropriately in each assembly process.

[0051]

Since the present invention is configured as described above, it has the following effects.

The transmission of the present invention uses a simple planetary gear having only a sun gear and a planetary gear, and has a small number of parts. Therefore, the number of causes of failure is small, miniaturization is easy, and installation space is small. There is a feature that can do.

Since the planetary gear reduction mechanism itself has a continuously variable transmission function of interposing a fluid, it is characterized in that a smooth transmission can be performed.

Since the transmission mechanism of the present invention has a structure that can cope with a thrust load, it is easy to make the transmission vertical in consideration of the method of mounting the main body.

Since the main body of the transmission is easy to miniaturize, the transmission can be integrated with the electric motor by considering the main body casing and the input shaft structure.

In the first embodiment, the control valve can be easily operated from the fully closed state to the fully opened state by operating the handle. Therefore, it is possible to easily and continuously transmit the rotation to the output shaft in the range from stop to full rotation. Is possible. It is considered that a similar handle operation mechanism can be provided in the third embodiment. It is considered that automatic operation such as rotation speed control can be performed by replacing the handle with an electric operating device.

In the third and fourth embodiments, the input side,
Further, by selecting the shape of the planetary gear on the output side, it is possible to realize a transmission mechanism more suitable for use conditions, and thus it is possible to provide a continuously variable transmission suitable for a wide range of applications.

[Brief description of the drawings]

 1 to 7 show the drawings according to the first embodiment.

FIG. 1 is a longitudinal sectional view of a transmission.

FIG. 2 is a sectional view of the transmission taken along the line AA in FIG. 1;

FIG. 3 is a sectional view of the transmission taken along the line BB in FIG. 1;

FIG. 4 is a cross-sectional view of the transmission taken along the line C-C in FIG. 1, showing a state in which a main body casing lid 6 is removed.

FIG. 5 is a partially detailed view of a conduction hole and a control valve portion related to FIG. 2;

FIG. 6 is a sectional view taken along line A1-A1 of FIG. 5;

FIG. 7 is a bird's-eye view for illustrating the principle of the transmission according to the first embodiment, schematically illustrating the transmission; 8, 9, 10, and 11 show drawings according to the second embodiment.

FIG. 8 is a longitudinal sectional view of the transmission.

FIG. 9 is a sectional view taken along the line DD in FIG. 8;

FIG. 10 is a sectional view taken along the line D′-D ′ of FIG. 8 and shows another example of the gear configuration.

FIG. 11 is a bird's-eye view for illustrating the principle of the transmission according to the second embodiment, schematically illustrating the transmission; 12 to 17 show drawings for the third embodiment.

FIG. 12 is a longitudinal sectional view of the transmission.

13 is a sectional view taken along the line HH of the transmission shown in FIG.

FIG. 14 shows the transmission E of FIGS. 10 and 11;
It is -E sectional drawing.

FIG. 15 shows the F of the transmission with respect to FIGS. 10 and 11;
It is -F sectional drawing.

FIG. 16 shows the G of the transmission with respect to FIGS. 10 and 11;
It is -G sectional drawing.

FIG. 17 is a bird's-eye view for illustrating the principle of the transmission according to the third embodiment, schematically illustrating the transmission; 18 to 21 show the drawings according to the fourth embodiment.

FIG. 18 is a longitudinal sectional view of the transmission.

19 is a sectional view taken along the line KK of the transmission relating to FIG. 20.

FIG. 20 shows the transmission I for FIGS. 18 and 19;
FIG.

FIG. 21 shows the J of the transmission for FIGS. 18 and 19;
It is -J sectional drawing.

[Explanation of symbols]

Reference numerals 1 to 20 denote the reference numerals in the drawings of the first embodiment. DESCRIPTION OF SYMBOLS 1 Input shaft 1a Input shaft flange portion 1b Gear meshing gap portion of input shaft flange portion 1c Gear meshing gap portion of input shaft flange portion 1d Projection portion fitted to control disk of input shaft flange portion 2 Output shaft 2a Output shaft Sun gear 3 Planetary gear 4 Gear housing lid 5 Main casing 5a Projection of input bearing of main casing 6 Main casing lid 7 Control valve 8 Abnormal pressure adjusting valve 9 Control disk 10 Screw for fixing control valve 11 Screw ring 12 External teeth Wheel 13 worm gear retainer 14 worm gear 14a worm gear shaft insertion joint 15 handle 16 screw plug with vent hole 17 screw plug 18 screw for fixing body casing lid 19 screw for fixing gear housing lid 20 worm gear retainer fixing Screws 31 to 36 are designated by reference numerals in the drawings for the second embodiment. 31 input shaft 31a, 31a 'input shaft flange 31b, 31b' input shaft flange gear meshing gap 31c, 31c 'input shaft flange gear meshing gap 31d, 31d' working fluid passage hole 31e 31e 'Conducting hole for hydraulic fluid 32 Output shaft 32a, 32a' Sun gear 33, 33 'for output shaft Planetary gear 34 Bearing board 35 Main casing 35a Connection port for outflow of hydraulic fluid 35b Connection port for inflow of hydraulic fluid 36 Main body The casing lids 41 to 66 are denoted by reference numerals in the drawings for the third embodiment. Reference Signs List 41 input shaft 41a input-side sun gear 42 output shaft 42a output-side sun gear 43 input-side planetary gear 44 output-side planetary gear 45 gear housing 45a input-side hydraulic fluid discharge gap 45b input-side hydraulic fluid inflow 45c Gap for inflow of hydraulic fluid on the output side 45d Gap for drainage of hydraulic fluid on the output side 45e Inflow side conduction hole of control valve 45f Exhaust side conduction hole of control valve 45g For moving hydraulic fluid from 45d to 45b Conductive hole 46 Input side gear housing cover 46a Annular communication hole between input side working fluid discharge gap 46b Spline portion of input side gear housing cover 47 Output side gear housing cover 47a Output side working fluid inflow gap Annular communication hole between parts 47b Communication groove to control valve spring chamber 47c Communication hole for abnormal pressure regulating valve 48 Body casing 49 Input body casing lid 50 Force-side main body casing cover 51 Reverse rotation prevention device 52 Control valve 53 Input-side bearing 54 Output-side bearing 55 Input-side bearing retainer 56 Output-side bearing retainer 57 Screw plug with vent hole 58 Screw plug 59 Pressure regulating valve 60 Reverse rotation Screws for fixing the protective device 61 Screws for fixing the main body casing lid on the input side 62 Screws for fixing the main body casing lid on the output side 63 Screws for fixing the gear housing lid on the input side 64 Screws for fixing the gear housing lid on the output side 65 Screws for fixing the bearing on the input side 66 Screws for fixing the bearing on the output side 81 to 104 are the same as those in the drawings of the fourth embodiment. 81 Input shaft 81a Input side sun gear 81b Inflow conduction hole 81c Discharge conduction hole 82 Output shaft 82a Output side sun gear 83 Input side planetary gear 84 Output side planetary gear 85 Gear housing 85a Input side operation Gap for liquid discharge 85b Gap for inflow of hydraulic fluid on input side 85c Gap for inflow of hydraulic fluid on output side 85d Gap for hydraulic fluid discharge on output side 85e Conductive hole for hydraulic fluid inflow 85f 85d Hydraulic fluid from 85d to 85b Of the gearbox 86 Input gear housing lid 86a Input-side hydraulic fluid discharge hole 86b Spline portion of the input gear housing lid 87 Output gear housing lid 88 Body casing 89 Input body casing lid 89a Inlet connection port for hydraulic fluid 89b Outlet connection port for hydraulic fluid 90 Main body casing lid on output side 91 Reverse rotation prevention device 92 Reverse rotation prevention device Fixing screw 93 Input side bearing 94 Output side bearing 95 Input side bearing retainer 96 Output side bearing retainer 97 Screw plug with vent hole 98 Screw plug 99 Input side bearing retainer fixing screw 100 Output bearing Screw for holding down the fixing 101 Screw for fixing the body casing lid on the input side 102 Screw for fixing the body casing lid on the output side 103 Screw for fixing the gear housing lid on the input side 104 Screw for fixing the gear housing lid on the output side

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[Procedure amendment]

[Submission date] February 4, 2002 (2002.2.4)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Full text

[Correction method] Change

[Correction contents]

[Document Name] Statement

[Title of the Invention] Fluid control continuously variable transmission

[Claims]

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission in a power transmission device for general industrial machines, construction machines, automobiles and the like.

[0002]

2. Description of the Related Art Conventionally, continuously variable transmissions have been used in various fields, such as industrial machines, construction machines, and automobiles, and there are various types of continuously variable transmissions. In the mechanical friction transmission type, a conical rotating body and a ring-shaped transmission ring pressed against it are combined to continuously move the diameter of the friction transmission action point.In the hydraulic type, a combination of a variable displacement pump and a hydraulic motor or input from the prime mover A method of controlling the rotation of one element of the planetary gear mechanism that receives rotation by a hydraulic stepless transmission mechanism to obtain an output rotation that is continuously variable from other output gear elements, or giving output rotation to the torque converter from the prime mover, There is a drive transmission mechanism for an automobile that switches the ring gears of several sets of planetary gear mechanisms to obtain different reduction ratios by a brake mechanism to realize a continuously variable transmission according to the characteristics of the prime mover. However, each of them is complicated and has many components.

[0003]

In order to achieve stepless deceleration with a conventional planetary gear mechanism and a transmission composed of a fluid rotating machine or the like, the number of components is large, the structure is complicated, and the installation space is large.

[0004]

The working fluid is filled in a plurality of sets of planetary gear mechanisms having different sizes each composed of a sun gear and a planetary gear housed in a rotatable gear housing, and input into the planetary gear mechanism by an input rotation. Means is to control the flow of the generated hydraulic fluid and apply it to the planetary gear mechanism on the output side to continuously change the output rotation.

[0005] Two sets of planetary gear mechanisms of different sizes, each composed of several planetary gears meshing with a sun gear and external teeth, are housed coaxially in a rotatable gear housing, facing the input side and the output side, respectively. .

The sun gear shaft on the input side slides from one of the rotation centers in the hermetically sealed gear housing, and the sun gear shaft on the output side slides from the other, and is rotatably supported by bearings of the main body casing to the outside. Penetrate to form an input shaft and an output shaft, respectively.

Since the bearing of the planetary gear housed in the gear housing is supported in the gear housing, the revolution of the planetary gear and the rotation of the gear housing are the same. Before and after the meshing portion between each planetary gear and the sun gear in the gear housing, there is provided a gap for discharging and flowing the working fluid.

The rotatable gear housing accommodated in the main body casing is engaged with the reverse rotation prevention device fixed in the main body casing and the projection of the gear housing lid by a spline, and rotates only in the same direction as the input and output rotations. It becomes possible. The working fluid filled in the gear housing is discharged by one of the meshing portions of the planetary gears and is fed by the input rotation from the sun gear on the input side, and flows in on the opposite side.

In the first embodiment, the discharge of the hydraulic fluid generated by the input-side planetary gear mechanism passes through the conduction path in the input-side gear housing lid, and joins in the conduction path in the input shaft, and the bearing of the input shaft. Nearby, it is led to a connection port to the outside of the transmission main body through a conduction path of the input side main body casing.

[0010] Each of the passages for the hydraulic fluid, which communicates with each of the pressure receiving gaps of the gear meshing portion of the output-side sun gear mechanism, that is, the gap for generating the output rotation, passes through the gear housing and passes through the input shaft. And then through the shaft, through the conduction path of the input side main body casing, to the connection port to the outside of the transmission main body.

The flow of the hydraulic fluid discharged from the gear meshing portion on the input side is controlled by a control mechanism outside the transmission, flows again into the transmission, and flows into the pressure receiving gap of the planetary gear mechanism on the output side. It acts to give output rotation. The rotational force applied to the output shaft by the hydraulic fluid and the rotational force generated in the gear housing by the pressure of the discharge flow of the hydraulic fluid generated by the input-side gear mechanism as the revolving force of the planetary gear are combined to produce output rotation. .

The hydraulic fluid that has acted on the gear meshing portion on the output side is conveyed to the meshing portion for the discharging action adjacent to the rotation of the gear, and passes through the conductive path provided in the gear housing wall to cause the suction action on the input side. It flows into a certain gear meshing portion, moves further to the gear meshing portion of the output side on the input side, and is again sent to a control mechanism outside the transmission to circulate.

When the flow of the hydraulic fluid is stopped by the control mechanism, the hydraulic fluid in the gear housing is stationary, so that the input and output planetary gears cannot rotate on the sun gear,
The gear housing and sun gear rotate together. The input rotation becomes the output rotation without being decelerated, and the reduction ratio becomes 1.

In the sun gear rotating with the same shaft torque, the pressure of the hydraulic fluid generated at the meshing portion with the planet gear is inversely proportional to the reference pitch circle diameter of the sun gear, and the discharge amount is proportional. The thickness of the gear in the axial direction is inversely proportional to the discharge pressure of the hydraulic fluid, and is proportional to the amount of discharge, that is, the amount of displacement due to meshing of the gears.

In the two sets of planetary gear mechanisms on the input side and the output side, the reference pitch circle diameter of the sun gear on the output side is twice as large as that on the input side, and the axial thickness of the gears of the planetary gear mechanism on the output side is doubled. Under the condition that the input side planetary gear mechanism is twice as large as the input side planetary gear mechanism, when the flow path of the control mechanism is fully opened, the discharge amount of the hydraulic fluid generated in the input side planetary gear mechanism becomes maximum and the reduction ratio is large. It acts on the gear meshing portion that generates output rotation on the output side.

At this time, ignoring the pressure loss and the like that the hydraulic fluid receives in the conduction path and the like, and ignoring the difference in the displacement of the hydraulic fluid due to the difference in the gear configuration having a different shape, it is assumed that the difference is equal to the input rotation. Output rotation is 1/4 rotation, torque is 4
You will get twice the output. The gear housing receives a reverse rotation force due to the reaction force of the output rotation, but is stopped by the reverse rotation prevention device.

When the flow of the hydraulic fluid is gradually reduced from the fully opened state by the control mechanism, the flow of the hydraulic fluid acting on the planetary gear mechanism on the output side starts to decrease, and the effect on the rotational force having a large reduction ratio is reduced. The increase in the pressure of the hydraulic fluid due to the resistance of the control mechanism increases the revolution force of the planetary gear on the input side, that is, the rotation of the gear housing, and gradually changes to high rotation and low torque, which are transmitted to the output shaft. The output shaft continuously changes the speed between a reduction ratio of 1 when the flow path is fully closed and a reduction ratio of 1/4 when the flow path is fully opened by operating the control mechanism.

By separately installing a hydraulic fluid control mechanism outside the transmission main body, there is an advantage that maintenance such as heat radiation for preventing a rise in the temperature of the hydraulic fluid during operation and replacement of the hydraulic fluid is facilitated. In addition, even when a plurality of transmissions are connected in series to form a speed reduction mechanism that obtains a wide reduction ratio, it is considered that the operation by the hydraulic fluid control mechanism can be easily realized.

In the second embodiment, the hydraulic fluid of the first embodiment is controlled outside the transmission. On the other hand, a control valve is provided inside the transmission to automatically and continuously change the load on the output shaft. Having. Fig. 10 shows the basic principle in a bird's-eye view.

A gap for discharging the working fluid of the planetary gear meshing portion on the input side and a gap for the working fluid flowing in the planetary gear meshing portion on the output side, that is, a gap for rotating the output of the sun gear. , A gap between each of the gaps is communicated with a conduction path in the gear housing, and an automatic control valve that increases and decreases the flow rate in proportion to the inflow pressure is provided in the path, and the pressure of the hydraulic fluid at the inflow section of the control valve is provided. When the pressure increases, the valve element moves to increase the flow rate.

The flow due to the discharge of the hydraulic fluid generated at the meshing portion of the input side planetary gear receives the resistance of the control valve and generates pressure. In response to the pressure, a resistance is given to the rotation of the planetary gear, causing it to revolve and rotate the gear housing.

The hydraulic fluid that has passed through the control valve acts on a meshing portion that generates an output rotation of the output side planetary gear mechanism. The planetary gear mechanism on the output side has a gear configuration that generates lower rotation and higher torque than the planetary gear mechanism on the input side.

The rotational force of the gear housing obtained by the pressure of the hydraulic fluid before passing through the control valve, and the two rotational forces provided by the hydraulic fluid that has passed through the control valve at the gear mesh portion on the output side are:
The output is combined by the planetary gear mechanism on the output side, and the output rotation is obtained.

When no load is applied to the output shaft, the planetary gear mechanism on the output side rotates freely and has no reaction force. Therefore, the pressure generated at the meshing portion for discharging the hydraulic fluid causes the rotating portion such as the gear housing to idle. Is not enough to act on the control valve to open the valve body, the control valve will remain closed and the hydraulic fluid in the gear housing will not flow. The input rotation rotates integrally with the gear housing and the output shaft, and the reduction ratio becomes 1.

Conversely, when the output shaft is subjected to the maximum load, the pressure at which the hydraulic fluid is discharged from the input side planetary gear mechanism is maximized by the rotational force transmitted from the gear housing, and the control valve is fully opened. At the same time, the flow rate of the hydraulic fluid from the input side is maximized, and flows into the gear meshing portion that performs the output rotation action. All power from the input shaft is transmitted to the output shaft by the hydraulic fluid in the gear housing.

At this time, the input side and the output side planetary gears only rotate, and the gear housing receives the revolving force in the opposite direction to the output rotation of the output side sun gear, but is stopped by the reverse rotation preventing device. . The rotation of the output shaft becomes the maximum torque and the minimum rotation speed in the combination of the planetary gear mechanisms.

Between the two sets of planetary gear mechanisms having different configurations, for example, the reference pitch circle diameter of the output-side sun gear having the same gear configuration as that of the first embodiment is set to be twice as large as that of the input side, and the axial sun direction of the gear is set. Assuming that the thickness is twice the thickness of the input side, the input side functions as a pump and the output side functions as a motor, and the output rotation is approximately 1/4 rotation and the torque is four times the output of the input rotation.

When the load on the output shaft gradually decreases, the opening of the control valve also decreases in proportion to the amount of hydraulic fluid passing therethrough. Therefore, the rotational force of the input shaft reduces the distribution of the rotational force having a large reduction ratio generated at the meshing portion of the planetary gears on the output side to the rotational force having a small reduction ratio applied to the gear housing.
That is, the distribution of the planetary gears to the orbital force is increased. These respective rotational forces are gradually transmitted to the output shaft at a high rotation speed and a low torque. When the output shaft is in the no-load state, the speed is continuously variable between the reduction ratio 1 and the reduction ratio 1/4 in the maximum load state according to the load.

The working fluid that has acted on the gear meshing portion on the output side via the control valve moves with the rotation of the gear to the meshing portion for the adjacent discharging action, and passes through a conduction path provided in the gear housing wall, thereby entering the input side. Flows into the gear meshing portion having a suction action, and further moves to a gap portion having a discharge action. The hydraulic fluid will circulate again.

In one planetary gear mechanism, it is desirable that the transmission of the force between the sun gear and the plurality of planetary gears meshing with the sun gear operate under uniform conditions. For this reason, an annular communication passage is provided in the gear housing lid, and an opening is formed between the gear meshing gaps that operate in the same manner so that the pressure condition of the working fluid is uniform. Therefore, even if the pressure characteristics are different among the plurality of control valves, uniform power transmission is achieved between each planetary gear and the sun gear.

The hydraulic fluid in the spring chamber flows out and in according to the movement of the valve body of the control valve. The hydraulic fluid is guided to the gear meshing portion on the output side by a communication groove provided in the gear housing lid on the output side. Has become.

In the case where the control valve is housed in the gear housing to seal the working fluid, the working fluid may expand due to a rise in temperature due to operation. It is desirable to install In the second embodiment, it is installed on the gear housing lid on the output side. Also, since the hydraulic fluid is subjected to pressure according to the load of the gear at the discharge part of the meshing part of the gear, the sliding parts such as the gear and the housing are manufactured precisely to prevent leakage of the hydraulic fluid, It is desirable to properly install O-rings and oil seals.

The third embodiment differs from the second embodiment in that a gear change operation mechanism using a steering wheel is installed in a type in which a control valve is built in the gear housing of the second embodiment. The planetary gear mechanism is the same as that of the second embodiment, but the output rotation is set by operating the handle provided outside the transmission from the model of the second embodiment in which the continuously variable speed is automatically changed according to the load of the output shaft. It is possible to do.

The ring-shaped control disk is arranged so as to face the gear housing cover surface on the output side, and is fitted with a projection on the gear housing cover surface to obtain rotational force, but slides movably in the axial direction. Further, an interlocking shaft with the control valve body penetrating the output side gear housing lid is joined to the control disk at an end portion, so that it is integrally moved in the axial direction.

The center of the control disk fits into the U-shaped groove of the screw wheel and slides and rotates, but the axial movement is restricted by the screw wheel. The inner diameter of the screw ring is assembled with the outer surface of the part forming the bearing housing protruding inside the main body casing lid on the input side and parallel screws, and moves in the axial direction according to the rotation of the screw wheel, and the opening degree of the control valve and It has a proportional structure.

The external gear wheel has an inner diameter assembled with the outer shape of the screw wheel by an axially movable spline, and meshes with the worm gear. The shaft of the worm gear is connected to a handle provided outside the main casing of the transmission, and the rotation of the handle causes the worm gear to rotate the screw wheel via the external gear wheel, thereby moving the control disk in the axial direction and controlling. The structure is linked to the opening of the valve. Therefore, the output rotation can be set by operating the steering wheel.

[0037]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings based on Embodiments 1, 2, and 3.

In the first embodiment, FIG. 1, FIG.
In the figure, a sun gear 2 of an output shaft 2 is mounted on a gear housing 5.
a and the planetary gears 4 are incorporated in the respective housing portions, and the output gear housing lid 7 is attached with screws 24.
In the gear housing 5 before and after the gear meshing portion of the planetary gear mechanism on the output side, a gap 5c for inflow of hydraulic fluid and a gap 5d for discharge of hydraulic fluid are provided.

1, 2 and 3, the output side of the input shaft 1 penetrates through the center of the gear housing 5 and is freely rotatable by a bearing provided at the center of the sun gear of the output shaft 2. The sun gear 1 a of the input shaft 1 is also accommodated in the gear housing 5. The planetary gear 3 on the input side is incorporated into each housing of the gear housing 5, and the gear housing lid 6 on the input side is attached with screws 23.

In FIGS. 1, 2, 3, and 4, the gear housing 5 before and after the gear meshing portion of the planetary gear mechanism on the input side has a gap 5a for discharging the working fluid. A space 5b for inflow of the hydraulic fluid is provided. In addition, conduction paths 5e provided inside the gear casing 5 communicating with the gap 5c for the hydraulic fluid inflow on the output side are connected to and merge with the conduction paths 1b in the input shaft, pass through the inside of the input shaft 1, and are close to the bearing 13. Is opened at a position communicating with a connection port 9a provided on the main body casing lid 9 on the input side of the main body. A communication path 5f is provided between the output-side gap 5d and the input-side gap 5b.

A conduction path 6 provided inside the input-side gear housing cover 6 communicating with the gap 5a for discharging the hydraulic fluid on the input side.
“a” is connected and connected to the conduction path 1 c in the input shaft, passes through the inside of the input shaft 1, and is opened at a position communicating with a connection port 9 b provided in the main body casing lid 9 on the input side.

In FIGS. 1 and 2, a reverse rotation prevention device 11 is attached to the input side main body casing lid 9 with screws 12. The input shaft 1 of a rotating body that is an integral assembly of the assembled input shaft 1, output shaft 2, gear housing 5, input-side gear housing cover 6, and output-side gear housing cover 7.
Is inserted from the inside of the main body casing lid 9 on the input side, and at the same time, the central protruding portion of the gear housing lid 6 on the input side and the anti-reverse device 11 are fitted to the spline portion 6b and assembled.

The bearing 13 of the input shaft is mounted on the housing of the input shaft 1 and the housing 9 of the main body casing 9 on the input side.
5 is fixed with screws 19. The main body casing 8 and the main body casing lid 9 on the input side are fixed with screws 21. The main body casing cover 10 on the output side is attached to the main body casing 8 with screws 22.
Fix with. The output shaft bearing 14 is mounted on the output shaft 2 and the housing of the output side main body casing lid 10, and the output side bearing retainer 16 is fixed with screws 20.

A screw plug 17 with a vent hole is provided at the upper part of the main body casing 8, and a screw plug 18 is provided at the lower part. Other oil seals, O-rings, etc. are appropriately attached in each assembly process.

In the second embodiment, FIG. 5, FIG. 6, FIG.
9, the control valve 42 is connected to the gear housing 35.
Attach. A sun gear 32a of the output shaft 32;
The planetary gears 34 are incorporated into respective housing portions of the gear housing 35.

The gear housing 35 before and after the gear meshing portion
Is provided with a gap 35c for the inflow of the working fluid and a gap 35d for the discharge of the working fluid. The gap 35c has a conduction path 35f from the control valve 42, and the gap 35d has an output side gear housing cover 37. Are provided with communication passages 37c communicating with the abnormal pressure adjusting valves 49 to be incorporated in each of them.

The gear housing cover 37 is provided with a bearing for the planetary gear 34 on the output side, an annular communication passage 37a, and a communication groove 37b to the control valve spring chamber. The output-side gear housing cover 37 is attached to the gear housing 35 with the screw 54 and sealed.

In FIG. 5 and FIG.
Is passed through the center of the gear housing 35, and is rotatably fitted to a bearing portion provided at the center of the sun gear of the output shaft 32. At the same time, the sun gear 31a and the planetary gear 33 on the input side are respectively connected to the gear housing 35. And the input-side gear housing lid 36 is attached with screws 53 and sealed.

In the gear housing 35 before and after the gear meshing portion of the planetary gear mechanism on the input side, a gap 3 for discharging the working fluid is provided.
5a and a gap 35b for inflow of the hydraulic fluid are provided. In the gap 35a, a conduction path 35e to the control valve 42 and a gap 35b are provided.
A conduction path 35g communicating with the gap b on the output side is provided. The input-side gear housing lid 36 is provided with an annular communication passage 36a communicating between the gaps for the hydraulic fluid discharge on the input side.

5 and 6, a reverse rotation preventing device 41 is screwed on the inner surface of the main body casing cover 39 on the input side.
Attach at 0. The assembled input shaft 31, output shaft 32, gear housing 35, input-side gear housing cover 36, and output-side gear housing cover 37 are combined with the input shaft 31 of the rotating body to form an input-side main body casing cover 39.
Of the gear housing cover 3 on the input side
6 and the reverse rotation prevention device 41 with the spline portion 36.
Fit to b and assemble. The bearing 43 is attached to the housing of the input shaft 31 and the housing of the main body casing cover 39 on the input side, and the bearing retainer 45 is fixed with the screw 55.

The main casing 38 and the main casing lid 39 on the input side are assembled with screws 51. Further, the main body casing cover 40 on the output side is screwed to the main body casing 38 with screws 52.
Assemble at The bearing 44 is mounted on the output shaft 32 and the housing of the main body casing cover 40 on the output side.
6 is fixed with screws 56. A screw plug 47 with a vent hole is provided at an upper portion of the main body casing 38, and a screw plug 48 is provided at a lower portion.
Other oil seals, O-rings, etc. are appropriately attached in each assembly process.

In the third embodiment, the transmission shown in the second embodiment is provided with an operation mechanism interlocked with a control valve, and the rotation is externally controlled. Only the transmission operation mechanism will be described. 11 and 12, a worm gear holder 63 in which a worm gear 65 and an external gear wheel 64 are assembled is fixed to the inner surface of the main body casing cover 61 on the output side with screws 72. The handle shaft 66 is inserted from the upper part of the main body casing lid 61, and is inserted and connected to the worm gear shaft joint portion 65a to attach the handle 67.

In FIGS. 11, 12, and 13, a control disk 69 is screwed into a parallel screw portion 61a with a screw wheel 68 slidably mounted in a U-shaped groove, and at the same time, an inner diameter of an external gear wheel 64. Fitting at the spline portion 68a.
In assembling the main body casing lid 61 and the main body casing in which the interlocking parts for shifting operation are assembled, the interlocking shaft 70 of the control valve penetrating the projection 62a of the gear housing lid 62 and the output side gear housing lid 62 is controlled. Fit into each assembly part of the disk 69. Assembly work hole 6
1b, the shaft end of the interlocking shaft 70 is fixed to the control disk 69 with the fixing screw 71.

[0054]

Since the present invention is configured as described above, it has the following effects.

According to the transmission of the present invention, by selecting a combination of gear sizes of a plurality of planetary gear mechanisms housed in the gear housing, a transmission mechanism having characteristics suitable for use conditions is realized. We believe that we can provide a continuously variable transmission.

By changing the type of the control valve of the hydraulic fluid used in the transmission of the present invention, a continuously variable transmission having different characteristics can be easily realized according to the purpose of use. We think that we can offer machine.

In the continuously variable transmission having the structure shown in the first embodiment, the control of the hydraulic fluid can be performed separately from the transmission main body. Is characterized in that rotation control with different characteristics can be realized.

By installing equipment for exchanging hydraulic fluid, radiating heat, purifying, etc. between the transmission main body and the control mechanism, maintenance of the transmission can be easily performed, so that long-term continuous operation can be realized. There is.

In the continuously variable transmission having the structure shown in the third embodiment,
It is possible to replace the handle part of the type that shifts with the handle installed outside the transmission body by an electric actuator, and it can be used for various applications because the output rotation can be controlled remotely by electric signals. Can be

In the present invention, since the planetary gear transmission mechanism itself has a continuously variable transmission function by interposing a fluid, when used in an automatic drive transmission mechanism of an automobile or the like, the conventional torque converter becomes unnecessary and the transmission mechanism is eliminated. Has the feature that it can be downsized and the installation space can be reduced.

Since the transmission of the present invention can achieve a continuously variable transmission with a simple configuration, the number of causes of failures is small, the size can be easily reduced, and a continuously variable transmission integrated with the electric motor can be easily realized. It is possible.

BRIEF DESCRIPTION OF THE DRAWINGS FIGS. 1 to 4 show drawings according to the first embodiment.

FIG. 1 is a longitudinal sectional view of a transmission.

FIG. 2 is a longitudinal sectional view of the transmission related to CC in FIG. 3;

FIG. 3 AA of the transmission with respect to FIG. 1 and FIG.
It is sectional drawing.

FIG. 4 is a BB diagram of the transmission relating to FIG. 1 and FIG. 2;
It is sectional drawing. FIGS. 5 to 10 show the drawings according to the second embodiment.

FIG. 5 is a longitudinal sectional view of the transmission.

FIG. 6 is a longitudinal sectional view of the transmission related to GG in FIG. 7;

FIG. 7 shows the transmission DD of FIG. 5 and FIG. 6;
It is sectional drawing.

FIG. 8 is a transmission EE with reference to FIGS. 5 and 6;
It is sectional drawing.

FIG. 9 is a transmission F-F relating to “FIG. 5” and “FIG. 6”;
It is sectional drawing.

FIG. 10 is a bird's-eye view for illustrating the principle of the transmission according to the second embodiment, schematically illustrating the transmission; FIGS. 11 to 13 show drawings according to the third embodiment.

FIG. 11 is a longitudinal sectional view of the transmission.

FIG. 12 is a sectional view taken along the line HH in FIG. 11;

FIG. 13 is a sectional view taken along the line II of FIG. 11;

[Description of References] Reference numerals 1 to 24 denote reference numerals in the drawings of the first embodiment. DESCRIPTION OF SYMBOLS 1 Input shaft 1a Sun gear of input shaft 1b Conductive path of hydraulic fluid inflow in input shaft 1c Conductive path of hydraulic fluid discharge in input shaft 2 Output shaft 2a Sun gear of output shaft 3 Planetary gear on input side 4 Output side Planetary gear 5 Gear housing 5a Input-side working fluid discharge gap 5b Input-side working fluid inflow gap 5c Output-side working fluid inflow gap 5d Output-side working fluid discharge gap 5e Inside gear housing Conductive path for hydraulic fluid inflow 5f Conductive path between input side and output side gap 6 Input side gear housing lid 6a Conductive path for hydraulic fluid discharge inside input side gear housing lid 6b Spline of input side gear housing lid Unit 7 Gear housing lid on output side 8 Body casing 9 Body casing lid on input side 9a Connection port for conduction path for hydraulic fluid inflow 9b Connection port for conduction path for hydraulic fluid discharge 10 Main body casing lid on output side 1 REFERENCE SIGNS LIST 1 reverse rotation preventing device 12 screw for fixing reverse rotation preventing device 13 input shaft bearing 14 output shaft bearing 15 input shaft bearing retainer 16 output shaft bearing retainer 17 screw stopper with vent hole 18 screw stopper 19 input shaft bearing retainer Screws for fixing 20 Bearing fixing screws for output shaft 21 Screws for fixing the main body casing lid on the input side 22 Screws for fixing the main body casing lid on the output side 23 Screws for fixing the gear housing lid on the input side 24 Output side Screws 31 to 56 for fixing the gear housing cover are denoted by reference numerals in the drawings of the second embodiment. Reference Signs List 31 input shaft 31a input shaft sun gear 32 output shaft 32a output shaft sun gear 33 input-side planetary gear 34 output-side planetary gear 35 gear housing 35a input-side hydraulic fluid discharge gap 35b input-side hydraulic fluid inflow 35c Gap for hydraulic fluid inflow on the output side 35d Gap for hydraulic fluid discharge on the output side 35e Conduction path for hydraulic fluid discharge on the input side 35f Conduction path for hydraulic fluid inflow on the output side 35g Between the input side and the output side Conduction path between gaps 36 Gear housing lid on input side 36a Annular communication path between gaps for hydraulic fluid discharge on input side 36b Spline part of gear housing lid on input side 37 Gear housing lid on output side 37a Operation on output side Annular communication path between liquid inflow gaps 37b Communication groove to control valve spring chamber 37c Communication hole for abnormal pressure regulating valve 38 Body casing 39 Input body casing Ring cover 40 Output side main body casing lid 41 Reverse rotation prevention device 42 Control valve 43 Input shaft bearing 44 Output shaft bearing 45 Input side bearing retainer 46 Output side bearing retainer 47 Screw plug with vent hole 48 Screw plug 49 Abnormal pressure Adjusting valve 50 Screw for fixing the reverse rotation prevention device 51 Screw for fixing the body casing lid on the input side 52 Screw for fixing the body casing lid on the output side 53 Screw for fixing the gear housing lid on the input side 54 Gear housing on the output side Screws for fixing the lid 55 Screws for fixing the bearing on the input side 56 Screws for fixing the bearing on the output side 61 to 71 denote the reference numerals in the drawings of the third embodiment. 61 Output side main body casing lid 61a Parallel screw part of output side main body casing lid 61b Assembly work hole 62 Output side gear housing lid 62a Projection part of gear housing lid 63 Worm gear holder 64 External gear wheel 65 Worm gear 65a Worm gear shaft joint 66 Handle shaft 67 Handle 68 Screw wheel 68a Spline portion of screw wheel and external gear wheel 69 Control disk 70 Interlocking shaft of control valve 71 Screw for fixing interlocking shaft of control valve 72 Worm gear retainer Fixing screw

[Procedure amendment]

[Submission date] February 4, 2002 (2002.2.4)

[Procedure amendment 1]

[Document name to be amended] Drawing

[Correction target item name] All figures

[Correction method] Change

[Correction contents]

FIG.

FIG. 2

FIG. 3

FIG. 4

FIG. 5

FIG. 6

FIG. 7

FIG. 8

FIG. 9

FIG. 10

FIG. 11

FIG.

FIG. 13

[Procedure amendment]

[Submission date] May 27, 2002 (2005.2.
7)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Full text

[Correction method] Change

[Correction contents]

[Document Name] Statement

[Title of the Invention] Fluid control continuously variable transmission

[Claims]

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission in a power transmission device for general industrial machines, construction machines, automobiles and the like.

[0002]

2. Description of the Related Art Conventionally, continuously variable transmissions have been used in various fields, such as industrial machines, construction machines, and automobiles, and there are various types of continuously variable transmissions. In the mechanical friction transmission type, a conical rotating body and a ring-shaped transmission ring pressed against it are combined to continuously move the diameter of the friction transmission action point.In the hydraulic type, a combination of a variable displacement pump and a hydraulic motor or input from the prime mover A method of controlling the rotation of one element of the planetary gear mechanism that receives rotation by a hydraulic stepless transmission mechanism to obtain an output rotation that is continuously variable from other output gear elements, or giving output rotation to the torque converter from the prime mover, There is a drive transmission mechanism for an automobile that switches the rotation of the ring gears of several planetary gear mechanisms having different reduction ratios by a brake mechanism to realize a continuously variable transmission according to the characteristics of the prime mover.

In order to obtain a continuously variable transmission with a conventional fluid rotating machine, for example, a transmission in which a planetary gear mechanism is combined with a torque converter, the number of components is large, the structure is complicated, and the installation space is large. If a system in which fluid is directly applied to the planetary gear mechanism itself to obtain a continuously variable transmission is possible, there is an advantage that the mechanism can be simplified and the installation space can be reduced. In order to achieve this, there are several technologies in Japanese and foreign patents that apply a fluid to a planetary gear mechanism housed in a rotatable gear housing to obtain a continuously variable transmission that causes a change in relative rotation. .

[0004]

A continuously variable transmission having a structure in which several sets of planetary gear mechanisms are housed in a conventional rotatable gear housing and a fluid is applied to change the relative rotation of the planetary gears. In the technical documents described above, there are problems that are not preferable in practice, such as a large number of gears, energy loss related to a complicated flow path of a working fluid, and a large installation space.

In particular, in the conventional basic technology of the continuously variable transmission, the rotation of the gear housing given by the input rotation, that is, the revolution of the planetary gear and the flow of the hydraulic fluid conducted to the meshing portion between the sun gear and the planetary gear are described. The output rotation is steplessly changed by combining with the rotation of the planetary gears by controlling. That is, a part of the power obtained by the input rotation is consumed in the process of controlling and circulating the hydraulic fluid in accordance with the speed change condition, resulting in a large energy loss, which has been a problem in practice.

[0006]

According to the present invention, in order to solve this problem, one of two sets of planetary gear mechanisms housed in a rotatable gear housing has, for example, an output side having a large size set in accordance with a gear ratio. The static pressure of the hydraulic fluid is effectively applied to the meshing portion between the sun gear and the planetary gear on the output side as a gear motor that operates the hydraulic fluid generated by the small planetary gear mechanism on the other input side at a low pressure. , By means of gearing with the resultant force of the revolution of the planetary gear by the input rotation to obtain the output rotation

Also, two sets of planetary gear mechanisms housed in a rotatable gear housing are arranged adjacent to each other with a partition wall interposed therebetween, and a conduction hole is provided in the partition wall to shorten the moving distance of the circulating hydraulic fluid, thereby reducing the energy due to fluid resistance. The structure minimizes the loss.

In a system in which the transmission continuously circulates the hydraulic fluid in order to rotate at a certain speed ratio, energy consumption of the fluid is continuously generated. Also, when the path through which the hydraulic fluid flows is long and complicated, the pressure loss of the fluid increases, so that it is necessary to sufficiently consider the structure.

There is a method of reducing the static pressure difference in the system by reducing the static pressure difference in the system by reducing the energy consumption of the working fluid acting on the gear meshing portion by closing the working fluid circulation circuit. In the case of a structure that can be obtained, energy loss due to fluid pressure loss and the like is inevitable. Therefore, it is necessary to minimize the flow of the working fluid at the reduction ratio actually used. The transmission also has the problem of minimizing energy loss by efficiently converting the input power as much as possible.It is necessary to consider the energy loss due to mechanical friction, etc. desirable.

In the present invention, the hydraulic fluid discharged from the input side planetary gear mechanism which functions as a gear pump when the load on the output shaft is large is engaged with the gear of the output side planetary gear mechanism which operates at a low pressure having a large reduction ratio. Since it flows into the section to generate the action of output rotation, it is possible to efficiently convert the energy obtained by the hydraulic fluid into a rotation action and circulate it.

When a continuously variable transmission is used for power transmission of a vehicle, a low-speed high-torque transmission is generally transmitted to an output shaft when the vehicle starts from a stop, and gradually accelerates to shift to a high-speed low torque. . Therefore, the present invention has a structure in which the ratio of the low-rotation high-torque output by the hydraulic fluid at the time of starting is increased, the rotating action of the hydraulic fluid is reduced at the high-speed low-torque output at the steady speed of the vehicle, and the fluid energy loss by the hydraulic fluid is reduced. did. At the maximum rotation speed, the flow of the hydraulic fluid is stopped, and the input shaft and the output shaft are directly connected to each other.

More specifically, the structure of the sun gear shaft on the input side and the sun gear shaft on the output side slide from one of the rotation centers in the sealed gear housing and the other, respectively.
Furthermore, it is rotatably supported by bearings of the main body casing and penetrates outside to form an input shaft and an output shaft, respectively.

Since the bearings of the planetary gears of the input and output planetary gear mechanisms housed in the gear housing are supported in the gear housing, the revolution of the planetary gear and the rotation of the gear housing are the same. Before and after the meshing portion between each planetary gear and the sun gear in the gear housing, there is provided a gap for discharging and flowing the working fluid.

The rotatable gear housing accommodated in the main body casing meshes with a reverse rotation prevention device fixed in the main body casing and a projection of the gear housing lid by a spline, and rotates only in the same direction as the input and output rotations. It becomes possible. The working fluid filled in the gear housing is discharged by one of the meshing portions of the planetary gears and is fed by the input rotation from the sun gear on the input side, and flows in on the opposite side.

In the first embodiment, the discharge of the hydraulic fluid generated by the input-side planetary gear mechanism passes through the conduction path in the input-side gear housing lid, and merges in the conduction path in the input shaft to form a bearing of the input shaft. Nearby, it is led to a connection port to the outside of the transmission main body through a conduction path of the input side main body casing.

[0016] Each of the passages for the hydraulic fluid that passes through the respective gaps receiving the pressure of the gear meshing portion of the sun gear mechanism on the output side, that is, the gaps that cause the output rotation, passes through the gear housing, and the passages in the input shaft. And then through the shaft, through the conduction path of the input side main body casing, to the connection port to the outside of the transmission main body.

The flow of the hydraulic fluid discharged from the gear meshing portion on the input side is controlled by a control mechanism outside the transmission, flows again into the transmission, and flows into the pressure receiving gap of the planetary gear mechanism on the output side. It acts to give output rotation. The rotational force applied to the output shaft by the hydraulic fluid and the rotational force generated in the gear housing by the pressure of the discharge flow of the hydraulic fluid generated by the input-side gear mechanism as the revolving force of the planetary gear are combined to produce output rotation. .

The hydraulic fluid acting on the gear meshing portion on the output side is conveyed to the meshing portion of the adjacent discharging action with the rotation of the gear, passes through a conduction path provided in the gear housing wall, and has a suction action on the input side. It flows into a certain gear meshing portion, moves further to the gear meshing portion of the output side on the input side, and is again sent to a control mechanism outside the transmission to circulate.

When the flow of the hydraulic fluid is stopped by the control mechanism, the hydraulic fluid in the gear housing is stationary, so that the input and output planetary gears cannot rotate on the sun gear,
The gear housing and sun gear rotate together. The input rotation becomes the output rotation without being decelerated, and the reduction ratio becomes 1.

In the sun gear rotating with the same shaft torque, the pressure of the working fluid generated at the meshing portion with the planetary gear is inversely proportional to the reference pitch circle diameter of the sun gear, and the discharge amount is proportional. The thickness of the gear in the axial direction is inversely proportional to the discharge pressure of the hydraulic fluid, and is proportional to the amount of discharge, that is, the amount of displacement due to meshing of the gears.

In the two sets of planetary gear mechanisms on the input side and the output side, the reference pitch circle diameter of the sun gear on the output side is twice that of the input side, and the axial thickness of the gears of the planetary gear mechanism on the output side is two times. Under the condition that the input side planetary gear mechanism is twice as large as the input side planetary gear mechanism, when the flow path of the control mechanism is fully opened, the discharge amount of the hydraulic fluid generated in the input side planetary gear mechanism becomes maximum and the reduction ratio is large. It acts on the gear meshing portion that generates output rotation on the output side.

At this time, ignoring the pressure loss and the like that the hydraulic fluid receives in the conduction path and the like, and ignoring the difference in the displacement of the hydraulic fluid due to the difference in the gear configuration having a different shape, and making them equal to each other, the input rotation is not affected. Output rotation is 1/4 rotation, torque is 4
You will get twice the output. The gear housing receives a reverse rotation force due to the reaction force of the output rotation, but is stopped by the reverse rotation prevention device.

When the flow of the hydraulic fluid is gradually reduced from the fully opened state by the control mechanism, the flow of the hydraulic fluid acting on the planetary gear mechanism on the output side starts to decrease, and the effect on the rotational force having a large reduction ratio is reduced. The increase in the pressure of the hydraulic fluid due to the resistance of the control mechanism increases the revolution force of the planetary gear on the input side, that is, the rotation of the gear housing, and gradually changes to high rotation and low torque, which are transmitted to the output shaft. The output shaft continuously changes the speed between a reduction ratio of 1 when the flow path is fully closed and a reduction ratio of 1/4 when the flow path is fully opened by operating the control mechanism.

By separately installing a hydraulic fluid control mechanism outside the transmission body, there is an advantage that maintenance such as heat radiation for preventing a rise in the temperature of the hydraulic fluid during operation and replacement of the hydraulic fluid is facilitated. In addition, even when a plurality of transmissions are connected in series to form a speed reduction mechanism that obtains a wide reduction ratio, it is considered that the operation by the hydraulic fluid control mechanism can be easily realized.

In the second embodiment, the hydraulic fluid of the first embodiment is controlled outside the transmission. On the other hand, a control valve is provided inside the transmission to automatically and continuously change the load on the output shaft. Having. Fig. 10 shows the basic principle in a bird's-eye view.

A gap for discharging the working fluid of the planetary gear meshing portion on the input side and a gap for the working fluid flowing in the planetary gear meshing portion on the output side, that is, a gap for rotating the output of the sun gear. An automatic control valve that increases and decreases the flow rate in proportion to the inflow pressure is provided in the passage through a conduction path in the gear housing, and when the pressure of the hydraulic fluid at the inflow portion of the control valve increases, the valve body is opened. It moves and increases the flow rate.

The flow due to the discharge of the hydraulic fluid generated at the meshing portion of the input side planetary gear receives the resistance of the control valve and generates pressure. In response to the pressure, a resistance is given to the rotation of the planetary gear, causing it to revolve and rotate the gear housing.

The hydraulic fluid that has passed through the control valve acts on a meshing portion that generates an output rotation of the output side planetary gear mechanism. The planetary gear mechanism on the output side has a gear configuration that generates lower rotation and higher torque than the planetary gear mechanism on the input side.

The rotational force of the gear housing obtained by the pressure of the hydraulic fluid before passing through the control valve and the two rotational forces applied by the hydraulic fluid that has passed through the control valve at the output side gear mesh portion are:
The output is combined by the planetary gear mechanism on the output side, and the output rotation is obtained.

When no load is applied to the output shaft, the planetary gear mechanism on the output side rotates freely and has no reaction force. Therefore, the pressure generated at the meshing portion for discharging the hydraulic fluid causes the rotating portion such as the gear housing to idle. Is not enough to act on the control valve to open the valve body, the control valve will remain closed and the hydraulic fluid in the gear housing will not flow. The input rotation rotates integrally with the gear housing and the output shaft, and the reduction ratio becomes 1.

Conversely, when the output shaft receives the maximum load, the pressure at which the working fluid is discharged from the planetary gear mechanism on the input side becomes maximum due to the rotational force transmitted from the gear housing, and the opening of the control valve is fully opened. At the same time, the flow rate of the hydraulic fluid from the input side is maximized, and flows into the gear meshing portion that performs the output rotation action. All power from the input shaft is transmitted to the output shaft by the hydraulic fluid in the gear housing.

At this time, the input-side and output-side planetary gears only rotate, and the gear housing receives a revolving force in the opposite direction to the output rotation of the output-side sun gear, but is stopped by the reverse rotation preventing device. . The rotation of the output shaft becomes the maximum torque and the minimum rotation speed in the combination of the planetary gear mechanisms.

Between the two sets of planetary gear mechanisms having different configurations, for example, the reference pitch circle diameter of the output-side sun gear having the same gear configuration as in the first embodiment is set to be twice as large as the input side, and Assuming that the thickness is twice the thickness of the input side, the input side functions as a pump and the output side functions as a motor, and the output rotation is approximately 1/4 rotation and the torque is four times the output of the input rotation.

When the load on the output shaft gradually decreases, the opening of the control valve also decreases proportionally, and the amount of hydraulic fluid passing therethrough decreases. Therefore, the rotational force of the input shaft reduces the distribution of the rotational force having a large reduction ratio generated at the meshing portion of the planetary gears on the output side to the rotational force having a small reduction ratio applied to the gear housing.
That is, the distribution of the planetary gears to the orbital force is increased. These respective rotational forces are gradually transmitted to the output shaft at a high rotation and a low torque. When the output shaft is in the no-load state, the speed is continuously variable between the reduction ratio 1 and the reduction ratio 1/4 in the maximum load state according to the load.

The hydraulic fluid that has acted on the gear meshing portion on the output side via the control valve moves with the rotation of the gear to the meshing portion for the adjacent discharge action, and passes through a conduction path provided in the gear housing wall, thereby entering the input side. Flows into the gear meshing portion having a suction action, and further moves to a gap portion having a discharge action. The hydraulic fluid will circulate again.

In one planetary gear mechanism, it is desirable that the transmission of the force between the sun gear and the plurality of planetary gears meshing with the sun gear operate under uniform conditions. For this reason, an annular communication passage is provided in the gear housing lid, and an opening is formed between the gear meshing gaps that operate in the same manner so that the pressure condition of the working fluid is uniform. Therefore, even if the pressure characteristics are different among the plurality of control valves, uniform power transmission is achieved between each planetary gear and the sun gear.

The hydraulic fluid in the spring chamber flows out and in according to the movement of the valve body of the control valve. The hydraulic fluid is guided to the gear meshing portion on the output side by a communication groove provided in the gear housing lid on the output side. Has become.

In the case where the control valve is housed in the gear housing to seal the working fluid, the working fluid may expand due to a rise in temperature during operation. It is desirable to install In the second embodiment, it is installed on the gear housing lid on the output side. Also, since the hydraulic fluid is subjected to pressure according to the load of the gear at the discharge part of the meshing part of the gear, the sliding parts such as the gear and the housing are manufactured precisely to prevent leakage of the hydraulic fluid, It is desirable to properly install O-rings and oil seals.

The third embodiment differs from the second embodiment in that the gear housing of the second embodiment is provided with a control valve, and a speed change operation mechanism using a handle is installed. The planetary gear mechanism is the same as that of the second embodiment, but the output rotation is set by operating the handle provided outside the transmission from the model of the second embodiment in which the continuously variable speed is automatically changed according to the load of the output shaft. It is possible to do.

The ring-shaped control disk is arranged so as to face the gear housing cover surface on the output side, and is fitted with a projection on the gear housing cover surface to obtain rotational force, but slides movably in the axial direction. Further, an interlocking shaft with the control valve body penetrating the output side gear housing lid is joined to the control disk at an end portion, so that it is integrally moved in the axial direction.

The central portion of the control disk fits into the U-shaped groove of the screw wheel and slides and rotates, but the axial movement is restricted by the screw wheel. The inner diameter of the screw ring is assembled with the outer surface of the part forming the bearing housing protruding inside the main body casing lid on the input side and parallel screws, and moves in the axial direction according to the rotation of the screw wheel, and the opening degree of the control valve and It has a proportional structure.

The external gear wheel has its inner diameter assembled with the outer shape of the screw wheel by a spline movable in the axial direction, and meshes with the worm gear. The shaft of the worm gear is connected to a handle provided outside the main casing of the transmission, and the rotation of the handle causes the worm gear to rotate the screw wheel via the external gear wheel, thereby moving the control disk in the axial direction and controlling. The structure is linked to the opening of the valve. Therefore, the output rotation can be set by operating the steering wheel.

[0043]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings based on Embodiments 1, 2, and 3.

In the first embodiment, FIG. 1, FIG.
In the figure, a sun gear 2 of an output shaft 2 is mounted on a gear housing 5.
a and the planetary gears 4 are incorporated in the respective housing portions, and the output gear housing lid 7 is attached with screws 24.
In the gear housing 5 before and after the gear meshing portion of the planetary gear mechanism on the output side, a gap 5c for inflow of hydraulic fluid and a gap 5d for discharge of hydraulic fluid are provided.

1, 2 and 3, the output side of the input shaft 1 penetrates the center of the gear housing 5 and freely fits into a bearing portion provided on the output shaft 2. The sun gear 1 a of the input shaft 1 is also housed in the gear housing 5. The planetary gear 3 on the input side is incorporated into each housing of the gear housing 5, and the gear housing lid 6 on the input side is attached with screws 23.

In FIG. 1, FIG. 2, FIG. 3, and FIG. 4, the gear housing 5 before and after the gear meshing portion of the planetary gear mechanism on the input side has a gap 5a for discharging the hydraulic fluid. A gap 5b for inflow of the working fluid is provided. In addition, conduction paths 5e provided inside the gear casing 5 communicating with the gap 5c for the hydraulic fluid inflow on the output side are connected to and merge with the conduction paths 1b in the input shaft, pass through the inside of the input shaft 1, and are close to the bearing 13. Is opened at a position communicating with a connection port 9a provided on the main body casing lid 9 on the input side of the main body. A communication path 5f is provided between the output-side gap 5d and the input-side gap 5b.

A conduction path 6 provided inside the input side gear housing lid 6 communicating with the gap 5a for discharging the hydraulic fluid on the input side.
“a” is connected and connected to the conduction path 1 c in the input shaft, passes through the inside of the input shaft 1, and is opened at a position communicating with a connection port 9 b provided in the main body casing lid 9 on the input side.

In FIGS. 1 and 2, a reverse rotation prevention device 11 is attached to the main body casing cover 9 on the input side with screws 12. The input shaft 1 of a rotating body that is an integral assembly of the assembled input shaft 1, output shaft 2, gear housing 5, input-side gear housing cover 6, and output-side gear housing cover 7.
Is inserted from the inside of the main body casing lid 9 on the input side, and at the same time, the central projection of the gear housing lid 6 on the input side and the reverse rotation prevention device 11 are assembled with the spline portion 6b.

The bearing 13 of the input shaft is mounted on the housing of the input shaft 1 and the housing 9 of the body casing 9 on the input side.
5 is fixed with screws 19. The main body casing 8 and the main body casing lid 9 on the input side are fixed with screws 21. The main body casing cover 10 on the output side is attached to the main body casing 8 with screws 22.
Fix with. The output shaft bearing 14 is mounted on the output shaft 2 and the housing of the output side main body casing lid 10, and the output side bearing retainer 16 is fixed with screws 20.

A screw plug 17 with a vent hole is provided at the upper part of the main body casing 8, and a screw plug 18 is provided at the lower part. Other oil seals, O-rings, etc. are appropriately attached in each assembly process.

In the second embodiment, FIGS. 5, 6, 7,
9, the control valve 42 is connected to the gear housing 35.
Attach. A sun gear 32a of the output shaft 32;
The planetary gears 34 are incorporated into respective housing portions of the gear housing 35.

The gear housing 35 before and after the gear meshing portion
Is provided with a gap 35c for the inflow of the working fluid and a gap 35d for the discharge of the working fluid. The gap 35c has a conduction path 35f from the control valve 42, and the gap 35d has an output side gear housing cover 37. Are provided with communication passages 37c communicating with the abnormal pressure adjusting valves 49 to be incorporated in each of them.

The gear housing lid 37 is provided with a bearing for the planetary gear 34 on the output side, an annular communication passage 37a, and a communication groove 37b to the control valve spring chamber. The output-side gear housing cover 37 is attached to the gear housing 35 with the screw 54 and sealed.

In FIG. 5 and FIG.
Is inserted through the center of the gear housing 35 so as to freely rotate and fit into a bearing provided on the output shaft 32. At the same time, the sun gear 31a and the planetary gear 33 on the input side are incorporated in each housing part, and The gear housing cover 36 is attached with screws 53 and sealed.

In the gear housing 35 before and after the gear meshing portion of the planetary gear mechanism on the input side, a gap 3 for discharging the working fluid is provided.
5a and a gap 35b for inflow of the hydraulic fluid are provided. In the gap 35a, a conduction path 35e to the control valve 42 and a gap 35b are provided.
A conduction path 35g communicating with the gap b on the output side is provided. The input-side gear housing lid 36 is provided with an annular communication passage 36a communicating between the gaps for the hydraulic fluid discharge on the input side.

5 and 6, a reverse rotation preventing device 41 is screwed on the inner surface of the main body casing cover 39 on the input side.
Attach at 0. The assembled input shaft 31, output shaft 32, gear housing 35, input-side gear housing cover 36, and output-side gear housing cover 37 are combined with the input shaft 31 of the rotating body to form an input-side main body casing cover 39.
Of the gear housing cover 3 on the input side
6 and the reverse rotation prevention device 41 with the spline portion 36.
Assemble with b. The bearing 43 is attached to the housing of the input shaft 31 and the housing of the main body casing cover 39 on the input side, and the bearing retainer 45 is fixed with the screw 55.

The main casing 38 and the main casing lid 39 on the input side are assembled with screws 51. Further, the main body casing cover 40 on the output side is screwed to the main body casing 38 with screws 52.
Assemble at The bearing 44 is mounted on the output shaft 32 and the housing of the main body casing cover 40 on the output side.
6 is fixed with screws 56. A screw plug 47 with a vent hole is provided at an upper portion of the main body casing 38, and a screw plug 48 is provided at a lower portion.
Other oil seals, O-rings, etc. are appropriately attached in each assembly process.

In the third embodiment, the transmission of the second embodiment is provided with a shift operation mechanism, and only the shift operation mechanism will be described. 11 and 12, a worm gear holder 63 in which a worm gear 65 and an external gear wheel 64 are assembled on the inner surface of a main body casing lid 61 on the output side.
Are fixed with screws 72. A handle shaft 66 is inserted from above the main body casing lid 61 and the worm gear shaft joint 65
Insert and connect to a and attach the handle 67.

The screw wheel 68 slidably mounted in the U-shaped groove with the control disk 69 is screwed into the parallel screw portion 61a, and at the same time, fitted with the spline portion 68a of the inner diameter portion of the external gear wheel 64. In assembling the main body casing lid 61 and the main body casing in which the gearshift operation interlocking parts are assembled, the interlocking shaft 70 of the control valve penetrated through the projection 62a of the gear housing lid and the output gear housing lid 62a.
Is fitted into the opening of each assembly part of the control disk 69. The shaft end of the interlocking shaft 70 is fixed to the control disk 69 with the fixing screw 71 from the assembly work hole 61b.

[0060]

Since the present invention is configured as described above, it has the following effects.

The present invention does not aim to use the hydraulic fluid as a resistance to the rotation of the gear element of the planetary gear mechanism for the braking action. That is, unlike the structure that causes a large energy loss due to the fluid, the hydraulic fluid is output at a low pressure. Because of the structure that works effectively on the rotating planetary gear mechanism, there is a feature that the loss of the input rotational power can be minimized.

Further, in the transmission according to the present invention, the two sets of planetary gear mechanisms are arranged adjacent to each other with a partition wall having a working fluid passage hole therebetween, so that the hydraulic fluid can smoothly move between the two planetary gear mechanisms. The feature is that energy loss due to hydraulic fluid can be reduced.

The transmission according to the present invention realizes a transmission mechanism more suitable for use conditions by selecting a combination of sizes of a plurality of planetary gear mechanisms housed in the gear housing.
We believe that we can provide a continuously variable transmission for a wide range of applications.

Since the planetary gear transmission mechanism itself has a continuously variable transmission function by interposing a fluid, when used in an automatic drive transmission mechanism of an automobile, a conventional torque converter becomes unnecessary and the transmission mechanism can be downsized. The feature is that the installation space can be reduced.

A handle part of a type that incorporates a control mechanism in the transmission body and performs gear shifting by operating the handle can be replaced with an electric operating machine, and the output rotation can be controlled remotely so that it can be used in various applications. Conceivable.

The transmission of the present invention has a simple structure in which the continuously variable transmission can be realized by two sets of planetary gear mechanisms composed of a planetary gear and a sun gear. And a continuously variable transmission integrated with the transmission.

BRIEF DESCRIPTION OF THE DRAWINGS FIGS. 1 to 4 show drawings according to the first embodiment.

FIG. 1 is a longitudinal sectional view of a transmission.

FIG. 2 is a cross-sectional view of the transmission taken along line CC of FIG. 3;

FIG. 3 AA of the transmission with respect to FIG. 1 and FIG.
It is sectional drawing.

FIG. 4 is a BB diagram of the transmission relating to FIG. 1 and FIG. 2;
It is sectional drawing. FIGS. 5 to 10 show the drawings according to the second embodiment.

FIG. 5 is a longitudinal sectional view of the transmission.

FIG. 6 is a sectional view taken along line GG of FIG. 7;

FIG. 7 shows the transmission DD of FIG. 5 and FIG. 6;
It is sectional drawing.

FIG. 8 is a transmission EE with reference to FIGS. 5 and 6;
It is sectional drawing.

FIG. 9 is a transmission F-F relating to “FIG. 5” and “FIG. 6”;
It is sectional drawing.

FIG. 10 is a bird's-eye view for illustrating the principle of the transmission according to the second embodiment, schematically illustrating the transmission; FIGS. 11 to 13 show drawings according to the third embodiment.

FIG. 11 is a longitudinal sectional view of the transmission.

FIG. 12 is a sectional view taken along the line HH in FIG. 11;

FIG. 13 is a sectional view taken along the line II of FIG. 11;

[Description of References] Reference numerals 1 to 24 denote reference numerals in the drawings of the first embodiment. DESCRIPTION OF SYMBOLS 1 Input shaft 1a Sun gear of input shaft 1b Conductive path of hydraulic fluid inflow in input shaft 1c Conductive path of hydraulic fluid discharge in input shaft 2 Output shaft 2a Sun gear of output shaft 3 Planetary gear on input side 4 Output side Planetary gear 5 Gear housing 5a Input-side working fluid discharge gap 5b Input-side working fluid inflow gap 5c Output-side working fluid inflow gap 5d Output-side working fluid discharge gap 5e Inside gear housing Conductive path for hydraulic fluid inflow 5f Conductive path between input side and output side gaps 6 Input side gear housing lid 6a Conductive path for hydraulic fluid discharge in input side gear housing lid 6b Spline of input side gear housing lid Unit 7 Gear housing lid on output side 8 Body casing 9 Body casing lid on input side 9a Connection port for conduction path for hydraulic fluid inflow 9b Connection port for conduction path for hydraulic fluid discharge 10 Main body casing lid on output side 1 REFERENCE SIGNS LIST 1 reverse rotation prevention device 12 screw for fixing reverse rotation prevention device 13 input shaft bearing 14 output shaft bearing 15 input shaft bearing retainer 16 output shaft bearing retainer 17 screw stopper with vent hole 18 screw stopper 19 input shaft bearing retainer Screws for fixing 20 Bearing fixing screws for output shaft 21 Screws for fixing the main body casing lid on the input side 22 Screws for fixing the main body casing lid on the output side 23 Screws for fixing the gear housing lid on the input side 24 Output side Screws 31 to 56 for fixing the gear housing cover are denoted by reference numerals in the drawings of the second embodiment. Reference Signs List 31 input shaft 31a input shaft sun gear 32 output shaft 32a output shaft sun gear 33 input-side planetary gear 34 output-side planetary gear 35 gear housing 35a input-side hydraulic fluid discharge gap 35b input-side hydraulic fluid inflow 35c Gap for hydraulic fluid inflow on the output side 35d Gap for hydraulic fluid discharge on the output side 35e Conduction path for hydraulic fluid discharge on the input side 35f Conduction path for hydraulic fluid inflow on the output side 35g Between the input side and the output side Conduction path between gaps 36 Gear housing lid on input side 36a Annular communication path between gaps for hydraulic fluid discharge on input side 36b Spline part of gear housing lid on input side 37 Gear housing lid on output side 37a Operation on output side An annular communication passage 37b between the liquid inflow gaps 37b A communication groove to the control valve spring chamber 37c A communication hole of the abnormal pressure regulating valve 38 Main body casing 39 Main body casing on the input side Ring cover 40 Output side main body casing lid 41 Reverse rotation prevention device 42 Control valve 43 Input shaft bearing 44 Output shaft bearing 45 Input side bearing retainer 46 Output side bearing retainer 47 Screw plug with vent hole 48 Screw plug 49 Abnormal pressure Adjusting valve 50 Screw for fixing the reverse rotation prevention device 51 Screw for fixing the body casing lid on the input side 52 Screw for fixing the body casing lid on the output side 53 Screw for fixing the gear housing lid on the input side 54 Gear housing on the output side Screws for fixing the lid 55 Screws for fixing the bearing on the input side 56 Screws for fixing the bearing on the output side 61 to 71 indicate the reference numerals in the drawings of the third embodiment. 61 Output side main body casing lid 61a Parallel screw part of output side main body casing lid 61b Assembly work hole 62 Output side gear housing lid 62a Projection part of gear housing lid 63 Worm gear holder 64 External gear wheel 65 Worm gear 65a Worm gear shaft joint 66 Handle shaft 67 Handle 68 Screw wheel 68a Spline portion of screw wheel and external gear wheel 69 Control disk 70 Interlocking shaft of control valve 71 Screw for fixing interlocking shaft of control valve 72 Worm gear retainer Fixing screw

Claims (5)

[Claims] A planetary gear is provided by filling a rotatable gear housing containing a planetary gear mechanism with hydraulic fluid and controlling a flow of hydraulic fluid generated at a planetary gear meshing portion obtained by input rotation and discharged. The drag acts on the meshing force of
A transmission characterized in that a change in rotation between gears is used as output rotation. 2. A plurality of planetary gears are housed in a flange portion having a gear housing portion which rotates integrally with an input shaft on a radius having a predetermined distance from an axis, and a central portion rotates integrally with an output shaft. The sun gear is housed and circumscribes the planetary gear,
In the front and rear of the gear meshing portion, there is a gap portion for inflow and discharge of hydraulic fluid, and further in a flange portion having a conduction hole communicating with the gap portion, a gear housing lid in which an output shaft is rotatably penetrated on an output side surface. 2. The transmission according to claim 1, wherein the transmission has a structure in which the sun gear, the planetary gear, and the meshing gap are sealed. 3. An input-side planetary gear mechanism and an output-side planetary gear mechanism having any or all of different shapes such as a gear diameter, a thickness, and a tooth shape are coaxially opposed to each other with a partition wall interposed therebetween. An input side surface and an output of a gear housing which are housed in a gear housing which is a rotating body, have a space for inflow and discharge of hydraulic fluid before and after each gear meshing portion, and further have a conduction hole communicating with the space. 2. The transmission according to claim 1, wherein the transmission shaft has a structure in which a side face is hermetically sealed by a gear housing lid rotatably penetrating an input shaft and an output shaft interlocked with each sun gear mechanism. 4. A structure in which a control valve is provided in a path of a conduction hole which is provided between a gap for a working fluid discharge provided in a gear meshing portion of a planetary gear mechanism and a gap for a working fluid inflow. "
The transmission according to claim 2 and claim 3. 5. A hydraulic fluid discharge space provided in a gear meshing portion of a planetary gear mechanism and respective conduction holes communicating with a hydraulic fluid inflow space are provided outside a transmission body through a rotary shaft. "Claim 1" and "Claim 2" of a structure respectively connected to the openings of
And the transmission according to claim 3.