JPS61236951A - Planet gear system two stage transmission - Google Patents

Abstract

PURPOSE:To permit two stage speed change in both forward and backward rotation by enabling a control member provided with an internal gear of a planet gear device to be selectively connected to a transmission frame or planet gear support member. CONSTITUTION:An annular support member 4 for rotatably supporting a planet gear 3 meshing with a sun gear 2 provided on a drive shaft 1 is unrotatably attached to a driven shaft 5. On the other hand, a control member 7 provided with an internal gear 6 is rotatably slidably fitted onto the drive shaft 1. And a connecting couple removably attached to the annular support member 4 and a controlling couple removably attached to a fixed portion such as a transmission frame 8 are provided on the control member 7 so that the connection and disconnection of the annular support member 4 and control member 7 and of the fixed portion and control member 7 are controlled by energizing and deenergizing an electromagnetic coil 9.

Description

[Detailed Description of the Invention] [Field of Industrial Application] This invention relates to a planetary gear type two-stage transmission device □ used for running lanes, traveling devices such as transport vehicles, or lifting machines such as electric chain blocks. It is.

[Prior art]

As an example of a conventional two-stage planetary gear transmission.

As disclosed in Japanese Utility Model Application No. 59-106764, it is equipped with a speed reduction mechanism consisting of two sets of planetary gear mechanisms connected in series, and a speed change control device that utilizes the planetary gear mechanism. The gear is fixed to the drive input shaft, and the sun gear of the first stage planetary gear mechanism in the speed reduction mechanism is fixed to the carrier supporting the planetary gear in the speed change control device, and the ring gear in the speed change control device is braked and There is said to be a structure that includes a friction brake that releases the brake, and a friction clutch that automatically and reversibly interlocks the ring gear with the drive input shaft in conjunction with the release of the friction brake. .

However, in the case of a planetary gear type two-stage transmission with this structure, two operating devices, a friction brake operating device and a friction clutch operating device, are required, and when one of the friction brake and the friction clutch is in the engaged state, Since it is necessary to control each of the operating devices in conjunction with each other so that the other is in the separated state, there is a problem that the configuration of the control device becomes complicated.

In addition, as another example of a planetary gear type two-stage transmission,
As disclosed in No. 9-29171, a planetary gear is rotatably attached to a carrier fixed to an output shaft, and a sun gear that meshes with the planetary gear is integrated into an input rotating body into which the output shaft is rotatably inserted. A one-way clutch is installed between the internal gear that meshes with the planetary gear and the transmission frame.

and an armature is attached to the carrier via an elastic body, a lining fixed to a flange of the input rotating body is interposed between the electromagnetic coil fixed to the transmission frame VC and the armature, and the electromagnetic coil is excited. Alternatively, a structure is known in which the speed of the transmission can be changed by demagnetizing the magnet.

However, in the case of a planetary gear type two-stage transmission with this structure,
Since a one-way clutch is provided between the internal gear and the transmission frame, it is possible to perform a two-speed shift when rotating the input rotating body in the forward direction, but when rotating the input rotating body in the reverse direction, it is possible to perform a two-speed shift. The problem is that it cannot be used.

[Purpose and structure of the invention]

The present invention provides a planetary gear type 2 which can advantageously solve the above-mentioned problems.
The purpose is to provide a step-change transmission device,
The gist of the invention is that an annular support member 4 that rotatably supports a planetary gear 3 that meshes with a sun gear 2 provided on a drive shaft 1 is wrapped in a non-rotatable manner with respect to a driven shaft 5; A control member 7 including an internal gear 6 meshing with the planetary gear 3 is rotatably and slidably fitted to the drive shaft 1, and the control member 7 has an annular support member 4.
A removable connecting joint and a transmission frame 8
A removable braking coupling part is provided for the fixed part such as, for excitation and demagnetization of one electromagnetic coil 9, for coupling the control member 7 to the annular support member 4 and for connecting the control member from the fixed part. 7, the control member 7 is coupled to the fixed portion, and the control member 7 is separated from the annular support member 4. .

〔Example〕

Next, the present invention will be explained in detail using illustrated examples.

1 to 3 show a first embodiment in which the present invention is applied to an electric chain hoist, in which
Drive shaft 1 extending in the left and right direction (in Figures 1 to 3)
The rear end is the rotor shaft 11 of the electric motor 10 with an electromagnetic brake.
A sun gear 2 is formed on the drive shaft 1, and the front end of the drive shaft 1 is connected to a hole in the rear end of a driven shaft 5 disposed on the same straight line as the drive shaft 1 through a bearing. A plurality of planetary gears 3 inserted into the sun gear 2 and meshing with the sun gear 2 are rotatably attached to an annular support member 4.
is fixed to a flange 12 provided at the rear end of the driven shaft 5 by bolts 13.

A control member 7 is provided with a frusto-conical friction surface 14 that expands toward the front on the outer periphery of the annular support member 4, and is made up of a cylindrical body 15 and an annular disc body 16 integrally provided at its front end. A cylindrical body 15 is rotatably fitted to the drive shaft 1 via a bearing 17, and is detachably attached to the frusto-conical friction surface 14 at the front portion of the outer circumferential side of the annular disk body 16.
A frusto-conical cylindrical friction ring 18 is fixedly fitted to the
The frusto-conical friction surface 14 and the frusto-conical cylindrical friction ring 1
8 and a connecting joint portion that can be freely attached and detached.

The internal gear 6 that meshes with the planetary gear 3 is fixed to the annular disk 16 by a port 19 inside the truncated conical cylindrical friction ring 18, and a transmission is mounted on the rear portion of the outer circumferential side of the annular disk 16. Inner flange 20 in frame 8
An annular friction plate 22 that is removably engaged with a friction surface 21 at the front of the brake is fixedly attached, and the friction surface 21 and the annular friction plate 22 form a removable braking joint.

The annular holding member 23 holding the electromagnetic coil 9 is
A bearing 26 is fitted inside an annular attracted body 25 made of a magnetic material that is in contact with the rear surface of the flange 20 and fixed by the bolt 24 and is arranged to face the rear surface of the annular holding member 23. It is fixed by a snap ring 27, and its bearing 26 is fitted and locked to a support ring 28 fitted on the rear outer periphery of the cylinder 15, and at the rear end of the cylinder 15.

The IJ song 9 (the thrust that engages with the rear end surface of the bearing 26) is fitted, and a snap ring 30 that locks the thrust ring 29 is fitted and locked.

A tightening spring 3 consisting of a helical spring for tightening the connecting joint between the annular disk body 16 and the support ring 28
1 is interposed between the recess of the annular holding member 23 and the recess of the annular attraction object 25.
A return spring 32 made of a helical spring is interposed to push back the electromagnetic coil 9 in a direction away from the electromagnetic coil 9 (backwards).

The driven shaft 5 is inserted into a hollow shaft 34 that is integrally provided with a load sheave 33 around which a load chain (not shown) is wound, and the hollow shaft 34 is supported by the frame of the electric chain hoist via a bearing 35. A gear reduction mechanism having a mechanical brake device is provided between the driven shaft 5 and the hollow shaft 34 to prevent the shear load sheep 33 from reversing due to the load of the suspended load. Since a gear reduction mechanism having a brake device is well known, illustration and detailed explanation thereof will be omitted.

In the device of the first embodiment, when the electromagnetic coil 9 is demagnetized, the annular attracted body 25 made of magnetic material is moved to the retracted position by the return spring 62, as shown in FIG. The suction body 25 causes the snap ring 27. Bearing 26
．． As the control member 7 is moved backward via the thrust ring 29° snap ring 60, the frusto-conical cylindrical friction ring 1B of the control member 7 separates from the frusto-cone friction surface 14 of the annular support member 4. Annular support member 4 and control section
The frictional connection between the member 7 and the annular disc 16 is released, and the friction surface 21 of the annular disc 16 is pressed against the friction surface 21 of the inner flange 20 of the transmission frame 8, thereby causing the control member 7 and the transmission The frame 8 is frictionally coupled.

When the electric motor 10 with an electromagnetic brake is operated in this state and the drive shaft 1 is rotated, the drive shaft 1 rotates the planetary gear 3 via the sun gear 2, and the planetary gear 3 rotates the circumference of the sun gear 2. The annular support member 4 that supports the shaft of the planetary gear 3 rotates at a low speed due to the rotation of the planetary gear 3, so the rotation of the drive shaft 1 is decelerated by the planetary gear mechanism and the rotation of the driven shaft 5 is reduced. 50 rotations of the driven shaft are further decelerated by a gear reduction mechanism having a mechanical brake device and transmitted to the load sheave 3'5IK.

Next, when the electromagnetic coil 9 is excited, as shown in FIG.
The annular attracted body 25 is attracted and moved to the forward position by the electromagnetic coil 9 against the force of the return spring 32, and the annular attracted body 25 is moved by the bearing 26° supporting ring 28 and the tightening spring 61. Since the control member 7 is moved forward through the control member 7, the annular friction plate 22 of the annular disk body 16 in the control member 7 separates from the friction surface 21 of the transmission frame 8, causing friction between the control member 7 and the transmission frame 8. The coupling is released, and the frusto-conical cylindrical friction ring 18 of the annular disc body 16 is pressed against the frusto-conical friction surface 14 of the annular support member 4, so that the annular support member 4 and the control member 7 are frictionally coupled. Ru.

When the electric motor 10 with an electromagnetic brake is operated in this state, the polycyclic support member 4. Planetary gear 3. Control member 7. Since the internal gear 6 is rotated together, the driven shaft 5 is rotated at a high speed, that is, at the same speed as the drive shaft 1, and therefore the load sheave 33 is also rotated at a relatively high speed.

4 and 5 show a second embodiment in which the present invention is applied to an electric chain hoist, in which an annular retainer in which an electromagnetic coil 9 is fitted and fixed to the front surface of a rear frame 36 of a transmission frame 8 is shown. The member 23 is brought into contact and fixed to the bolt 24.

The drive shaft 1 connected to the rotor shaft 11 of the electric motor 10 with an electromagnetic brake is supported by the rear frame 36 via a bearing 37, and is inserted through the annular holding member 23, and is disposed at the front of the annular holding member 23. Control member 7 made of magnetic material
is fitted onto the drive shaft 1 via a bearing 38, and an internal gear 6 is provided inside the front end of the control member 7.
A truncated conical cylindrical friction ring 18 that contracts toward the front is fixed to the outside of the front end of the control member 7, and a layer is detachably attached to the front friction surface of the annular holding member 26 on the rear surface of the control member 7. An annular friction plate 22 that is engaged with the annular friction plate 22 is solidly layered, and the friction surface and the annular friction plate 22 form a removable braking joint.

An annular support member 4 disposed at the front of the control member 7 is fitted onto the front end of the drive shaft 1 via a bearing 39, and the truncated conical cylindrical friction member is attached to the rear end of the annular support member 4. ring 18
A truncated conical friction surface 14 is provided to removably engage the truncated conical friction surface 14, and the truncated conical friction surface 14 and the truncated conical cylindrical friction ring 18 form a removably connecting coupling part. has been done.

At the rear of the annular support member 4, a sun gear 2 provided at the front of the drive shaft 1 and a planetary gear 3 meshing with the internal gear B are rotatably attached. The rear part of the fitted thrust bearing 40 is engaged with the stepped portion of the drive shaft 1, and the spring bearing ring 41 is fitted onto the drive shaft 1 and engaged with the front part of the thrust bearing 40.
A coupling 42, which is unrotatably fitted to the rear end of the driven shaft 5, is connected to the frame of the electric chain hoist between the tightening spring 31 and the control member 7. It is supported via a cross bearing 46, and its coupling 4
2 and the annular support member 4 are unrotatably connected via a joint ring 44.

The transmission mechanism between the driven shaft 5 and the load sheave 36 is the same as in the first embodiment.

In the device of the second embodiment, when the electromagnetic coil 9 is excited, the control member 7 is attracted and moved rearward against the force of the tightening spring 31, as shown in FIGS. 4 and 5. The frusto-conical cylindrical friction ring 18 of the member 7 is separated from the frusto-conical friction surface 14 of the annular support member 4, and the friction plate 22 at the rear end of the control member 7 is pressed against the front surface of the annular retaining member 23. , the control member 7 and the annular holding member 23 are frictionally coupled.

When the electric motor 10 with an electromagnetic brake is operated in this state, the rotation of the drive shaft 1 is decelerated by the planetary gear mechanism and transmitted to the driven shaft 5 as described above.

Next, when the electromagnetic coil 9 is demagnetized, the control member 7 is moved forward by the force of the tightening spring 31, and the annular friction plate 22 of the control member 7 is separated from the annular holding member 23. A frusto-conical cylindrical friction ring 18 is attached to the annular support member 4.
The annular support member 4 and the control member 7 are frictionally connected by pressing against the frusto-conical friction surface 14 of the annular support member 4 and the control member 7. When the electric motor 10 with an electromagnetic brake is operated in this state, the annular support member 4. Planetary gear 3. Since the control member 7 is rotated together, the driven shaft 5 is rotated at high speed, that is, at the same speed as the drive shaft 1.

6 and 7 show a third embodiment in which the present invention is applied to an electric chain hoist, in which a plurality of The clamping disc spring 45 is fitted, the rearmost clamping disc spring 45 is engaged with the stepped part of the drive shaft 1, and the support cylinder 46, which has a male thread in the middle, is attached to the drive shaft 1. The rear end of the support cylinder 46 is engaged with a tightening disc spring 45 at the frontmost part, and the male thread of the support cylinder 46 is fitted with a tightening force adjustment screw. The nut 47 is screwed together, and the claw pieces around the locking ring 48, which is unrotatably and slidably fitted into the support cylinder 46, are bent and fitted into the recesses around the nut 47. ing.

The internal gear 6 and the retaining ring 50 are sequentially superposed on the front part of the flange 49 connected to the front end of the cylinder 15, and the bolt 51
The control member 7 is constructed by multiple coupling, and the cylindrical body 15 of the control member 7 is supported by the support cylinder 46 via a bearing 52.

A friction plate 22 is fixed to the front surface of the retaining ring 50, and a plurality of planetary gears 3 meshing with the sun gear 2 provided at the front of the drive shaft 1 and the internal gear 6 can be rotated freely. The annular support member 4 is supported by the front end of the drive shaft 1 via a bearing 56, and the annular support member 4 is non-rotatably but slidably fitted to the rear end of the driven shaft 5. The front end of the annular support member 4 is engaged with the stepped portion of the driven shaft 5.

A friction ring 55 is fixed to the speed reduction unit frame 54 facing the outer peripheral side of the front surface of the annular friction plate 22, and a friction ring 55 is fixed to the rear part of the outer peripheral side of the annular support member 4 on the inner peripheral side of the front surface of the annular friction plate 22. Opposing friction surfaces 56 are provided, and the annular friction plate 22 and the friction ring 55 constitute a removable braking joint, and the annular friction plate 22 and the friction surface 56 form a removable connection joint. configured,
Further, the driven shaft 5 is rotatably and slidably supported by the variable speed reduction section frame 54 via a υ bearing 57.

The annular holding member 23 to which the electromagnetic coil 9 is fitted and fixed is fixed to the speed change reduction section frame 54, and the base end of the operating arm 59 is pivotally connected to the bracket 58 fixed to the speed change reduction section frame 54 by a pin 60. , the movable iron core 61 inserted into the electromagnetic coil 9 and the tip of the operating arm 59 are connected via a pin 62, and the operating arm 590
A protrusion 63 that engages with the front end surface of the driven shaft 5 is provided on the base end side, and a small diameter drive gear 64 provided on the driven shaft 5 is further provided.
A large-diameter intermediate driven gear 65 fixed to an intermediate shaft is engaged with the small-diameter intermediate driven gear 65 fixed to the intermediate shaft, and a large-diameter driven gear 67 fixed to a load shaft 66 is fixed to the small-diameter intermediate drive gear fixed to the intermediate shaft. A load sheave 33 around which a load chain is wound is integrally provided on the shaft 66.

In the device of the third embodiment, when the electromagnetic coil 9 is demagnetized, as shown in FIGS. 6 and 7, the tightening disc spring 45
Due to the force of the support cylinder 46. Tightening force adjustment nut 47. On the fourth day of the locking ring, the control member 7 is moved forward via the bearing 52, and the annular friction plate 2 fixed to the control member 7 is moved forward.
2 is pressed against a friction ring 55 fixed to the speed reduction part frame 54, the control member 7 and the speed change reduction part frame 54 are connected, and the friction surface 56 of the annular support member 4 is separated from the annular friction plate 22. ing.

When the electric motor 10 with an electromagnetic brake is operated in this state and the drive shaft 1 is rotated, the drive shaft 1 rotates the planetary gear 6 via the sun gear 2, and the planetary gear 3 turns around the sun gear 2. However, since the annular support member 4 supporting the shaft of the planetary gear 3 is rotated at low speed by the rotation of the planetary gear 3, the rotation of the drive shaft 1 is decelerated by the planetary gear mechanism and transmitted to the driven shaft 5. The rotation of the driven shaft 5 is further decelerated by the gear reduction mechanism and transmitted to the load sheave 63.

Next, when the electromagnetic coil 9 is energized, the movable iron core 61 is moved backward and the operating arm 59 is swung rearward, and the protrusion 63 of the operating arm 59 is attached to the annular support member via the driven shaft 5. 4 is pressed rearward, and the friction surface 56 of the annular support member 4 is press-bonded to the annular friction plate 22, and then the annular support member 4 is pressed against the force of the one disc spring 45 for tightening. The control member 7 is moved rearward, and the annular friction plate 22 of the control member 7 is pressed against the friction ring 5 of the speed reduction section frame 54.
Leave from 5.

When the electric motor 10 with an electromagnetic brake is operated in this state, the control member 7. Annular support member 4. Since the planetary gears 6 and the like are rotated together, the driven shaft 5 is rotated at a high speed, that is, at the same speed as the drive shaft 1, and therefore the load sheave 36 is also rotated at a relatively high speed.

Note that the present invention can also be implemented in a speed change device in a traveling device such as a traveling lane or a transport vehicle.

〔Effect of the invention〕

According to this invention, the sun tooth provided on the drive shaft 1! An annular support member 4 that rotatably supports a planetary gear 6 that meshes with the planetary gear 2 is non-rotatably mounted on the driven shaft 51C, and a control member 7 that includes an internal gear 6 that meshes with the planetary gear 3 is connected to the drive shaft 51C. The control member 7 is rotatably and slidably fitted to the shaft 1, and the control member 7 includes a removable coupling joint to the annular support member 4 and a removable braking joint to a fixed part such as the transmission frame 8. A coupling part is provided, by means of the excitation and demagnetization of one electromagnetic coil 9, the coupling of the control member 7 to the annular support member 4 and the separation of the control member 7 from said fixed part and the control member 7 relative to said fixed part. , and the control member 7 is separated from the annular support member 4. Therefore, even when the drive shaft 1 rotates in the forward direction or when the drive shaft 1 rotates in the reverse direction, only one By simply energizing and demagnetizing the electromagnetic coil 9, the planetary gear type transmission can be switched between high speed rotation and low speed rotation, and the planetary gear type transmission can be switched between forward rotation speed and reverse rotation speed. The control mechanism is relatively simple and can perform accurate switching control, and furthermore, the annular support member 4. Planetary gear6. Control member 7. Since the large mass part consisting of the internal gear 6 etc. starts rotating by the drive shaft 1,
It is possible to start the engine slowly, and therefore the effects such as reducing the shock when starting at high speed can be obtained.

[Brief explanation of drawings]

1 to 6 show a first embodiment in which the present invention is applied to a transmission section of an electric chain hoist, in which FIG. 1 is a partially cutaway vertical side view, and FIG. FIG. 3 is a longitudinal sectional side view showing a state in which the gear transmission is switched to low speed rotation, and FIG. 3 is a longitudinal sectional side view showing a state in which the planetary gear type two-stage transmission is switched to high rotation speed. Figures 4 and 5
The figures show a second embodiment in which the present invention is implemented in the transmission section of an electric chain hoist, in which Figure 4 is a partially cutaway vertical side view, and Figure 5 shows a planetary gear type two-stage transmission that rotates at low speed. FIG. 6 and 7 show a third embodiment in which the present invention is applied to a transmission section of an electric chain hoist, in which FIG. 6 is a partially cutaway vertical side view, and FIG. FIG. 3 is a longitudinal side view showing a state in which the speed change gear is switched to low speed rotation. In the figure, 1 is a drive shaft, 2 is a sun gear, 6 is a planetary gear, 4 is an annular support member, 5 is a driven shaft, 6 is an internal gear, 7 is a control member, and 8 is a transmission frame. 9 is an electromagnetic coil, 10 is an electric motor with an electromagnetic brake, 14
Has a truncated conical friction surface, 18t! A truncated conical cylindrical friction ring, 21 is a friction surface, 22 is an annular friction plate, 23 is an annular holding member, 25 is an annular attracted member made of magnetic material, 31 is a tightening spring, 62 is a return spring, 45 is a A tightening disc spring, 47 a tightening force adjustment knob), 54d a speed reduction unit frame, 55 a friction ring, 56 a friction surface, 59 an operating arm, and 61 a movable iron core.

Claims (1)

[Claims] A planetary gear 3 that meshes with a sun gear 2 provided on the drive shaft 1
An annular support member 4 rotatably supports a driven shaft 5.
A control member 7 is mounted non-rotatably on the drive shaft 1 and includes an internal gear 6 that meshes with the planetary gear 3. The control member 7 is rotatably and slidably fitted on the drive shaft 1.
is provided with a removable connecting joint to the annular support member 4 and a removable braking joint to a fixed part such as the transmission frame 8, and by excitation and demagnetization of one electromagnetic coil 9, such that the connection of the control member 7 to the annular support member 4 and the separation of the control member 7 from said fixed part and the connection of the control member 7 to said fixed part and the separation of the control member 7 from the annular support member 4 take place. A planetary gear type two-stage transmission device characterized by the following.