JP2003214518A - Electric speed change cylinder - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric speed change cylinder easily incorporated in a press machine and a caulking machine, while it is moved forward and backward at two speeds of a high and a low speed. <P>SOLUTION: A drive mechanism is electrically driven and a double screw mechanism 4 rotationally driven by a drive mechanism 2 consists of a first screw means 9 and a second screw means 10 different in screw pitch from that of the first screw means 9. The drive mechanism comprises a switching mechanism 5 to be switched from the drive force of the drive mechanism 2 to the first screw means 9 or the second screw means 10, which are different in screw pitch from each other; and an output shaft 3 to be switched to the first screw means 9 or the second screw means 10 of the double screw mechanism and perform linear reciprocating movement at two speeds of a high and a low speed. This constitution makes it compact and enables easy incorporation into a device to perform linear reciprocating movement. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electric transmission cylinder.

[0002]

2. Description of the Related Art Conventionally, a hydraulic cylinder is generally used for a device such as a press machine, a caulking machine, a press-fitting machine, a strain relief machine, etc., which performs processing by linear motion. It is used in all fields because hydraulic drive by a hydraulic cylinder can handle high speed and low speed and has a large driving force.
However, since a hydraulic device as a drive source has to be attached, the size of the device becomes large, and since hydraulic oil is used, the surroundings of the device are easily soiled with oil. For this reason, electric cylinders are often used instead of hydraulic cylinders in the processing of precision equipment and electronic equipment that are afraid of failure due to oil adhesion. However, the electric cylinder has a problem that it is difficult to switch the output within the stroke. Therefore, it is also attempted to set the high and low second speeds by assembling a transmission having a gear mechanism, or by assembling a high speed driving device and a low speed driving device. However, when the drive device is assembled for use in the device, the size of the drive device becomes large and the part projects from the outer shape of the cylinder, making it difficult to incorporate the device into a device such as a press machine, a caulking machine, a press-fitting machine, or a strain relief machine.

[0003]

SUMMARY OF THE INVENTION It is an object of the present invention to provide an electric speed change cylinder which can be advanced and retracted at high and low speeds and is compact and easy to be incorporated in a device such as a press machine or a caulking machine.

[0004]

In order to achieve the above-mentioned object, the present invention provides an electric drive mechanism, a first screw means rotatably driven by the drive mechanism, and a screw pitch between the first screw means. A double screw mechanism composed of different second screw means, a switching mechanism for switching the driving force of the drive mechanism to the first screw means or the second screw means, and the first screw of the double screw mechanism. Means or an output shaft which is switched to the second screw means to perform a linear reciprocating motion at high and low second speeds, and an electric speed changing cylinder in which the electric motor electrically controls the speed. In the invention according to claim 1 or 2, the electric transmission cylinder is provided with a first screw means, and the first screw means is screwed into an outer peripheral thread portion formed on the drive shaft of the drive mechanism and the outer peripheral thread portion. The inner peripheral thread is formed An electric speed changer cylinder including a screw body is defined as the invention of claim 3, and in the invention of claims 1 to 3, the second screw means is fixed to the output shaft and the screw portion of the outer periphery formed in the middle screw body to prevent rotation. And an outer threaded body formed with an inner threaded portion that is screwed into the outer threaded portion of the middle threaded body.
In the inventions 1 to 4, the switching mechanism includes a first clutch mechanism for locking the drive shaft to the first screw means at the end of high speed forward movement of the output shaft, and a first clutch mechanism for the drive shaft at the end of high speed backward movement of the output shaft. When the drive shaft is locked to the first screw means by the forward movement of the output shaft and the second clutch mechanism that is locked to the first screw means, the lock between the first screw means and the output shaft is released and the output shaft is driven backward. A fifth aspect of the invention is an electric transmission cylinder comprising a third clutch mechanism for releasing the lock between the first screw means and the output shaft when the shaft is locked by the first screw means. In the first
The clutch mechanism of (1) comprises an annular clutch pawl formed on the inner surface of the front end of the drive shaft, and an annular clutch pawl formed on the front end surface of the first screw means and detachable from the clutch pawl. A second aspect of the present invention is a cylinder, wherein a second clutch mechanism is an annular clutch pawl formed on a rear inner surface of a drive shaft, and a second clutch mechanism is formed on a rear end surface of a first screw means and is disengageable from the clutch pawl. According to the invention of claim 7, the third clutch mechanism has a circular clutch external gear formed on the outer peripheral surface of the tip of the first screw means and an output shaft. A circular clutch internal gear that is fixedly engaged with the clutch external gear and is disengageably engaged with the clutch internal gear, a first operating rod that projects from the tip of the clutch internal gear and retracts the clutch internal gear itself, and a second screw Means to slide itself An invention of claim 8 is an electric transmission cylinder comprising a second actuating rod, which is provided in the vehicle for advancing the clutch internal gear, and a spring mechanism for urging the clutch internal gear to mesh with the clutch external gear. .

[0005]

BEST MODE FOR CARRYING OUT THE INVENTION Next, preferred embodiments of the present invention will be described in detail with reference to FIGS. In the figure, reference numeral 1 denotes a tubular main body, a drive mechanism 2 is attached to a rear portion of the main body 1, and a tubular output shaft which is fixed to a front portion of the main body 1 by a key 1a to prevent rotation of the main body 1. 3 is inserted so that it can move back and forth. The main body 1 and the output shaft 3 are connected to each other via a double screw mechanism 4 to be described later, and the output shaft 3 is moved forward and backward at high and low second speeds. Further, the double screw mechanism 4 incorporates a switching mechanism 5 for switching the speed between high and low second speeds.
By switching the operating speed of the output shaft 3 between the high speed and the low speed, the output can be made small at the high speed and made large at the low speed.

As shown in FIGS. 1 to 5, the drive mechanism 2 comprises an electric motor 2a and a speed reducer 2b, and a drive shaft 6 extends forward from the speed reducer 2b. 7 is a drive shaft 6
Is a rear bearing, and the rear bearing 7 is a clutch body 1 described later.
The drive shaft 6 is supported via the shaft 3a, and is attached to the front end of the speed reducer 2b. Reference numeral 8 is a front bearing of the drive shaft 6. The front bearing 8 supports the drive shaft 6 through a clutch body 12a, which will be described later, and is mounted inside the cylindrical output shaft 3 so as to be movable back and forth. ing. The drive mechanism 2 is on / off controlled by a timer or a limit switch for position detection. Furthermore, the electric motor 2a
Is rotated at a constant speed, but the rotation speed may be electrically controlled by using an AC servo motor, an inverter control motor, or the like. By controlling the electric motor 2a, the speed of the output shaft 3 or The output can be set in detail.

As shown in FIGS. 6 and 7, the double screw mechanism 4 comprises a first screw means 9 and a second screw means 10, and the first screw means 9 is attached to the outer periphery of the drive shaft 6. It is composed of a formed threaded portion and an inner threaded body 9a having an inner periphery formed with a threaded portion to be screwed into the threaded portion.
The linear reciprocating motion is performed by the forward and reverse rotations of. Further, the drive shaft 6 and the middle screw body 9a are screwed by a ball screw 9b. Further, the second screw means 10 is composed of a screw portion formed on the outer periphery of the middle screw body 9a and an outer screw body 10a having a screw portion screwed on the screw portion formed on the inner periphery,
The outer screw body 10a performs a linear reciprocating motion by the forward and reverse rotations of the middle screw body 9a. Further, the flange 10c formed at the base end of the outer screw body 10a is locked to the base end of the output shaft 3. The outer screw body 10a and the middle screw body 9a are screwed by a ball screw 10b. Further, the screw pitch of the drive shaft 6 is set to be larger than the screw pitch of the outer screw body 10a, and the forward speed of the first screw means 9 is faster than the forward speed of the second screw means 10. Specifically, a middle screw body 9 screwed into the drive shaft 6
The screw pitch of a is 50 mm, and the screw pitch of the outer screw body 10a screwed into the middle screw body 9a is 5 mm.

Further, the switching mechanism 5 is composed of a first clutch mechanism 12, a second clutch mechanism 13 and a third clutch mechanism 14, and the first clutch mechanism 12 of the output shaft 3 is provided. The drive shaft 6 operates at the end of high-speed forward movement.
And the first screw means 9, and the second clutch mechanism 13 operates at the end of the high speed backward movement of the output shaft 3 to lock the drive shaft 6 and the first screw means 9. is there. The third clutch mechanism 14 releases the lock between the first screw means 9 and the output shaft 3 when the drive shaft 6 is locked to the first screw means 9 by the forward movement of the output shaft 3. Further, when the drive shaft 6 is locked to the first screw means 9 by the backward movement of the output shaft 3, the lock between the first screw means 9 and the output shaft 3 is released.

Further, as shown in FIGS. 6 and 7, the first clutch mechanism 12 is keyed to the tip of the drive shaft 6 and is supported in the output shaft 3 through a front bearing 8 so as to be movable back and forth. An annular clutch pawl 15 formed on the clutch body 12a and an annular clutch pawl 16 formed on the tip of the middle screw body 9a of the first screw means 9. The annular clutch pawl 15 has a saw-toothed cross section in which vertical stopper surfaces 15a are formed at intervals of 180 degrees. The annular clutch pawl 16 forms a pair with the clutch pawl 15, and has a vertical sawtooth-shaped cross section in which vertical stopper surfaces 16a that abut the vertical stopper surface 15a are formed at intervals of 180 degrees. Although 16 is engaged, the engagement is automatically disengaged at the time of reverse rotation. Clutch claws 15 and 16 to 1
The two ridges are arranged at 80 degree intervals so that when the clutch claws 15 and 16 are engaged, the claws are locked after rotating 180 degrees from the position where the crests of the clutch claws 15 and 16 start contacting each other. This is for ensuring the engagement of the clutch claws 15 and 16. The clutch pawl 16 is formed on the tip surface of a cylindrical body 16c that is key-fitted to the tip portion of the middle screw body 9a.

The second clutch mechanism 13 is shown in FIG.
As shown in FIG. 3, an annular clutch pawl 17 formed on the clutch body 13a attached to the rear portion of the drive shaft 6 via a rear bearing 7 and a rear end of the middle screw body 9a of the first screw means 9 are formed. And an annular clutch pawl 18 to be formed. The annular clutch pawls 17 have vertical stopper surfaces 1 at 180 degree intervals.
The vertical stopper surface 18a, which has a sawtooth-shaped cross section and is paired with the annular clutch pawl 18 and the clutch pawl 17, is in contact with the vertical stopper surface 17a.
It has a serrated cross section formed at intervals, and the clutch pawls 17 and 18 are engaged during reverse rotation, but automatically disengaged during normal rotation. Clutch claw 17, 1
No. 8 has two peaks at 180 degree intervals because the clutch pawl 17 is
In order to ensure the engagement of the clutch claws 17 and 18 by engaging the clutch claws 17 and 18 after 180-degree rotation from the position where the claw crests of the clutch claws 17 and 18 start contacting, the claws are locked. is there.

Further, the above-mentioned third clutch mechanism 14
As shown in FIGS. 8, 9, and 13, the circular clutch internal gear 20 a formed on the annular clutch body 20 key-fixed to the inner surface of the base portion of the output shaft 3 and the first screw means 9 A circular clutch outer gear 21 is formed on the outer peripheral surface of the tip of the middle screw body 9a, and the clutch inner gear 20a of the clutch body 20 and the clutch outer gear 21 are disengageably engaged with each other.

Reference numeral 22 denotes the clutch internal gear 2 of the clutch body 20.
0a is a first operating rod that projects from the front end of the clutch body 12a and contacts the flange 12b of the clutch body 12a to retract the clutch body 20, and the first operating rod 22 turns off the third clutch mechanism 14. It is a thing. Reference numeral 23 is a second operating rod for advancing the clutch body 20, and the second operating rod 23 is attached to the outer screw body 10a of the second screw means 10 so as to be movable back and forth. When the output shaft 3 is retracted, the operating rod 23 is brought into contact with the flange portion 13b formed on the clutch body 13a to slide the clutch body 20 forward, thereby turning off the third clutch mechanism 14.

Reference numeral 24 denotes a spring mechanism of the clutch body 20,
As shown in FIGS. 8 and 9, in the spring mechanism 24, the clutch body 20 is the clutch internal gear 20 of the third clutch mechanism 14.
The spring 25 includes a spring 25 for urging the clutch a and the clutch external gear 21 in a direction to always engage with each other, and a spring receiving ring 24a for receiving front and rear ends of the spring 25. 26 is a stopper of the spring receiving ring 24a attached to the middle screw body 9a of the first screw means 9, and the other receiving ring 24a uses the clutch external gear 21 as a stopper.

The structure thus constructed is shown in FIGS.
It shall be assembled to the frame 30 of the press machine or deburring machine shown in FIG. Then, when performing punching work or deburring work by the press machine, first, if the electric motor 2a of the drive mechanism 2 is driven, the driving force of the electric motor 2a is reduced.
The rotational force input to b and decelerated is transmitted to the drive shaft 6. By rotating the drive shaft 6, the double screw mechanism 4 is driven as shown in FIG.
At this time, the third clutch mechanism 14 of the switching mechanism 5 is shown in FIG.
As shown in (1), since the first screw means 9 and the output shaft 3 are locked by the urging force of the spring mechanism 24,
The middle screw body 9a of the first screw means 9 screwed into the large-pitch screw portion of the drive shaft 6 is advanced at high speed, and the output integrated with the middle screw body 9a of the first screw means 9 is output. The shaft 3 will also move forward at high speed. As a result, the output shaft 3 is advanced at high speed just before machining.

Then, as shown in FIG. 2, the first switching mechanism 5 is sent forward together with the first screw means 9.
As shown in FIG. 3, the clutch pawl 16 as the clutch mechanism 12 of FIG.
5 will be engaged. Simultaneously with this engagement, the first operating rod 22 protruding from the clutch body 20 comes into contact with the flange 12b of the clutch body 12a, and as shown in FIG. 8, the third clutch mechanism 14 of the switching mechanism 5 moves. Since the meshing between the clutch internal gear 20a and the clutch external gear 21 is released against the biasing force of the spring 25 of the spring mechanism 24, the drive shaft 6 and the intermediate screw body 9a of the first screw means 9 are both It will start turning around. The rotation of the middle screw body 9a that rotates together with the drive shaft 6 is the second screw means 10 having a small screw pitch.
Is transmitted to the outer screw body 10a. Since the outer screw body 10a is locked to the base end of the output shaft 3 via the flange 10c, the output shaft 3 advances at a low speed to generate a large output. In the press shown in FIG. 15, the output shaft 3
The punch 31 attached to the tip of the blank is inserted into the die 32 while generating a large force at a low speed, and the blank is pressed. In the deburring machine shown in FIG. 16, the cutter 33 attached to the tip of the output shaft 3 is advanced at a low speed to cut off the burr with a large force.

After such processing is completed, the drive mechanism 2 is reversely operated by the timer or the limit switch, so that the drive shaft 6 is reversely rotated. When the drive shaft 6 moves backward and backward, the clutch pawls 15 and 16 of the first clutch mechanism 12 are automatically disengaged, and the first actuating rod 22 is disengaged from the flange 12b. The third clutch mechanism 14 of the switching mechanism 5 is changed from the off state to the on state by the urging force of the spring 25 of the mechanism 24,
That is, as shown in FIG. 10, the clutch internal gear 20
The a and the clutch external gear 21 mesh with each other. Since the first screw means 9 is integrated with the output shaft 3 when the third clutch mechanism 4 is turned on, the output shaft 3 retreats at a high speed due to the large screw pitch of the first screw means 9 screwed into the drive shaft 6. As a result, the output shaft 3 returns to the old position at high speed.

The clutch pawl 17 formed on the clutch body 13a of the second clutch mechanism 13 by retreating the output shaft 3 is a clutch pawl 18 formed on the rear end of the middle screw body 9a of the first screw means 9. And will be engaged. Simultaneously with this engagement, the second operating rod 23, which is attached to the second screw means 10 so as to be movable back and forth, abuts on the flange portion 13b of the clutch body 13a, so that the second operating rod 23 abuts on the clutch body 20. The operating rod 23 of FIG. 6 pushes the clutch body 20 forward against the biasing force of the spring 25 of the spring mechanism 24. As a result, as shown in FIG. 9, the third clutch mechanism 14 is turned off, that is, the engagement between the clutch internal gear 20a and the clutch external gear 21 of the first screw means 9 is released. Therefore, the drive shaft 6 and the first screw means 9
Since the rotation of the drive shaft 6 is transmitted to the outer screw body 10a of the second screw means 10 having a small screw pitch, the output shaft 3 retracts at a low speed. This backward movement is performed by stopping the operation of the drive mechanism 2 by operating the timer or the limit switch.
The reason why the output shaft 3 is set to a low speed immediately before the stop is that if the drive mechanism 2 is stopped at a low speed, the drive mechanism 2 can be stopped surely without a brake mechanism and without giving a shock.

In the preferred embodiment, the first
Screw means 9 of the second screw means 10 of the ball screw 9b, 1
Although 0b is used to reduce the frictional resistance, it goes without saying that ordinary screws may be used. Further, in the preferred embodiment, the drive mechanism 2 is composed of the electric motor 2a and the speed reducer 2b, but it goes without saying that the speed reducer 2b may be omitted and only the electric motor 2a may be used.

[0019]

As is apparent from the above description, the present invention is such that the electric drive mechanism, the first screw means rotatably driven by the drive mechanism, and the first screw means have different screw pitches. A double screw mechanism comprising a second screw means, a switching mechanism for switching the driving force of the drive mechanism to the first screw means or the second screw means, and the first screw means or the second screw mechanism of the double screw mechanism. It is of course possible to use it for processing precision equipment and electronic equipment because it is electrically driven and there is no oil splattering because it is composed of an output shaft that is linearly reciprocated at high and low second speeds by being switched to the screw means. Therefore, the speed and the output can be switched between high and low second speed within the stroke. Moreover, since the compact shape that can be accommodated in the outer shape of the main body can be maintained, it can be easily incorporated into a press machine, a caulking machine, a press-fitting machine, or the like. Furthermore, since it is possible to move at high speed during non-processing, the total processing time can be shortened, and a large output can be generated at low speed, so that the range of application of processed products can be widened. As described in claim 2, the speed of the electric motor is electrically controlled, which has various advantages such that the range of application of the processed product can be further expanded. Therefore, the present invention is extremely significant in that it contributes to the development of the industry by solving the problems of the conventional electric transmission cylinder.

[Brief description of drawings]

FIG. 1 is a partially cutaway side view showing a preferred embodiment of the present invention.

FIG. 2 is a partially cutaway side view showing a high speed forward movement according to a preferred embodiment of the present invention.

FIG. 3 is a partially cutaway side view showing a low speed forward movement according to a preferred embodiment of the present invention.

FIG. 4 is a partially cutaway side view showing a high speed backward movement according to a preferred embodiment of the present invention.

FIG. 5 is a partially cutaway side view showing a low speed backward movement according to a preferred embodiment of the present invention.

FIG. 6 is an enlarged cross-sectional view showing a state just before meshing of the clutch in the preferred embodiment of the present invention.

FIG. 7 is an enlarged cross-sectional view showing a meshed state of the clutch in the preferred embodiment of the present invention.

FIG. 8 is an enlarged cross-sectional view showing a state in which the third clutch mechanism used in the preferred embodiment of the present invention is turned off by forward movement.

FIG. 9 is an enlarged cross-sectional view showing a state in which the third clutch mechanism used in the preferred embodiment of the present invention is turned off by retreating.

FIG. 10 is an enlarged sectional view showing an ON state of a third clutch mechanism used in the preferred embodiment of the present invention.

FIG. 11 is a front view showing the clutch body of the first clutch mechanism used in the preferred embodiment of the present invention.

FIG. 12 is a side view showing a clutch body of a first clutch mechanism used in a preferred embodiment of the present invention.

FIG. 13A of FIG. 7 showing a preferred embodiment of the present invention.
FIG.

FIG. 14B of FIG. 7 showing a preferred embodiment of the present invention.
It is a -B sectional view.

FIG. 15 is a partially cutaway front view showing a state in which a preferred embodiment of the present invention is incorporated in a press machine.

FIG. 16 is a partially cutaway front view showing a state in which a preferred embodiment of the present invention is incorporated in a deburring machine.

[Explanation of symbols]

2 drive mechanism 3 output axes 4 Double screw mechanism 5 Switching mechanism 6 drive shaft 9 First screw means 9a Middle screw body 10 Second screw means 10a External screw body 12 First clutch mechanism 13 Second clutch mechanism 14 Third clutch mechanism 15 clutch pawl 16 clutch pawl 17 Clutch claw 18 clutch pawl 20a clutch internal gear 21 Clutch external gear 22 First operating rod 23 Second operating rod 24 spring mechanism

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) H02K 7/06 H02K 7/06 AF term (reference) 3J056 AA02 BA03 BA04 BE07 CA02 CB03 CC03 DA05 FA13 GA05 GA26 3J062 AA21 AB22 AC07 BA12 BA29 CD22 CD50 CD56 CD79 5H607 BB01 CC03 DD03 DD19 EE02 EE10 EE22 EE24 EE31 EE53 EE56 GG07

Claims (8)

[Claims] 1. A double screw mechanism comprising an electric drive mechanism, a first screw means rotationally driven by the drive mechanism, and a second screw means having a different screw pitch from the first screw means. A switching mechanism for switching the driving force of the driving mechanism to the first screw means or the second screw means, and the first screw means or the second screw means of the double screw mechanism to switch between high and low second speeds. An electric speed change cylinder, comprising an output shaft that performs linear reciprocating motion. 2. The electric speed change cylinder according to claim 1, wherein the speed of the electric motor is electrically controlled. 3. The first screw means comprises an outer peripheral threaded portion formed on the drive shaft of the drive mechanism and an intermediate threaded body formed with an inner peripheral threaded portion to be screwed into the outer peripheral threaded portion. The electric transmission cylinder according to claim 1 or 2, characterized in that 4. A second screw means is formed on an outer peripheral threaded portion formed on the middle threaded body and an inner peripheral threaded portion which is fixed to the output shaft so as not to rotate and is screwed into the outer peripheral threaded portion of the middle threaded body. The electric transmission cylinder according to any one of claims 1 to 3, wherein the electric transmission cylinder comprises an externally threaded body. 5. A first clutch mechanism, wherein a switching mechanism locks the drive shaft to the first screw means at the end of high-speed advance of the output shaft, and a drive shaft to the first screw means at the end of high-speed reverse of the output shaft. When the drive shaft is locked to the first screw means by the forward movement of the output shaft and the second clutch mechanism for locking,
A third clutch for releasing the lock between the screw means and the output shaft, and for releasing the lock between the first screw means and the output shaft when the drive shaft is locked to the first screw means by retreating the output shaft. And a mechanism.
5. The electric speed change cylinder according to any one of 1 to 4. 6. A first clutch mechanism has an annular clutch pawl formed on the inner surface of the front end of the drive shaft, and an annular clutch pawl formed on the front end surface of the first screw means so as to be engageable with and disengageable from the clutch pawl. The electric speed change cylinder according to claim 5, comprising a clutch pawl. 7. A second clutch mechanism has an annular clutch pawl formed on the inner surface of the rear portion of the drive shaft, and an annular clutch pawl formed on the rear end surface of the first screw means so as to be engageable with and disengageable from the clutch pawl. The electric speed change cylinder according to claim 5, comprising a clutch pawl. 8. A third clutch mechanism is fixed to an output shaft of a circular clutch external gear formed on the outer peripheral surface of the tip of the first screw means, and is meshed with the clutch external gear so as to be disengageable. A circular clutch internal gear and a first clutch internal gear that is projected from the tip of the clutch internal gear and retracts the internal clutch gear itself.
Operating rod, a second operating rod slidably provided on the second screw means to move the clutch internal gear forward, and a spring mechanism for urging the clutch internal gear to mesh with the clutch external gear. The electric transmission cylinder according to claim 5, characterized in that.