TWI440516B - Main shaft driving device - Google Patents

Description

Spindle drive

The invention relates to a spindle driving device, in particular to a driving design of a spindle having a high and low gear shifting switch and a backlash eliminating mechanism, so that the spindle can be operated at a high speed without a backlash eliminating function, and has high and low gear shifting. The function can be widely used in general cutting processing; when the spindle is accurately positioned, the application of the precise position control of the spindle is achieved by initiating the backlash elimination function.

According to the previous rotary spindle system, as shown in the first figure, in order to be applicable to general-purpose machining with high speed, low torque and low speed and high torque, the drive group (5) usually needs to be shifted by the gearbox (51) for high and low speed. Switching, and then transmitting power to the main shaft (54) via the gear (53) of the drive shaft (52) to meet various cutting processing conditions; but generally the gearbox (51) is driven by the gear, and there is a backlash. Therefore, when the spindle (54) is positioned for positioning, the positioning is usually unable to achieve an accurate effect. Therefore, if the workpiece must be accurately positioned, the backlash eliminating mechanism needs to be used to correspond to the backlash problem, but usually the backlash eliminating mechanism is mostly It is only applied to the transmission of the feed shaft (as shown in the second figure). This transmission method uses the hydraulic cylinder (57) to push the helical gear (56) to perform the backlash elimination action, but the backlash elimination mechanism has no shifting. The function must increase the transmission torque through multiple stages of deceleration, so it cannot be applied to high speeds, and is mostly applied to the drive of the feed shaft. Therefore, if the spindle needs to be able to perform high-speed machining and low-speed precise position positioning, Usually, the machine tool market will adopt the design of built-in motor or direct transmission spindle, so that it can meet the needs of processing and precise positioning. However, due to the direct transmission factor, the spindle can only be cut at high speed or only at low speed.

In order to improve the above shortcomings, please refer to the third figure, the market has developed the concept of double-drive transmission, the double-drive transmission must be driven by a combination of two sets of gearboxes (61) and two sets of drive groups (6); The high-torque output can be obtained from the main shaft, and the two sets of drive groups can be adjusted with electrical control to achieve low-speed backlash-free transmission requirements. However, the high cost, space and electrical control are complex. In the industry, there is also the concept that the angle positioning function of the table during power-driven and milling processing of the rotary table is individually controlled (as shown in the fourth figure), which is driven by a spindle motor (62). a box (63) for causing the gearbox (63) to drive the table (64) to operate. When the table is required to be accurately positioned at an angle, the power is switched to the servo motor (65) on the other side to the servo motor (65). The angular positioning of the table is driven by a gear without backlash, but this method requires two sets of power-driven motors, resulting in high cost and complicated overall structure.

In the continuation, as disclosed in Japanese Patent No. 3725519 (P3729519), the content disclosed is a backlash eliminating mechanism design, which can solve the above problem, and drives the worktable by a single power source, and switches through the backlash elimination mechanism device. When the table is used for rotary turning, backlash is allowed, and during milling, the backlash is eliminated. The method is two spur gears with the same number of teeth and the same modulus but different tooth thickness, combined with the same shaft, and matched with the switching device to achieve the function of backlash elimination. Since the backlash elimination amount is fixed, the adjustment cannot be automatically compensated; and when the spindle has no backlash elimination to be operated at a high speed, the backlash due to the pitch error between the transmission gears cannot be eliminated, so there is no balanced drive during turning. The function.

In view of this, the inventors have been enriching the design and development of this related industry for many years. The actual production experience, in particular, provides a spindle drive to improve the lack of prior art, with a view to achieving better practical value.

The main object of the present invention is to provide a spindle driving device which is mainly provided with a spindle driving device having a high- and low-speed shifting switching and a backlash eliminating mechanism, so that the spindle can be operated at a high speed without starting the backlash eliminating function, and It has high and low-speed shifting function, which can be widely used in general cutting. When the spindle is accurately positioned, it can achieve the purpose of precise position control of the spindle by starting the backlash elimination function. Therefore, the spindle can be applied to It has a high- and low-speed shifting function, and requires a backlash to eliminate the machine tool spindle for precise position control purposes; the applied machinery is a floor-type boring and milling machine spindle, a vertical lathe table, a milling and turning machine table.

In order to achieve the above object, the present invention provides a spindle driving device, which has the following features and functions: it is mainly driven by a driving group and a backlash eliminating mechanism and a gearbox to drive two power output shafts, so that the two power output shafts drive the spindle In the operation, in the state where the backlash elimination function is not activated, since there is a back gap between the transmission gears, the high-speed operation of the main shaft can avoid the interference caused by the friction heat between the transmission gears, and the main shaft is transmitted through the transmission. With high and low-speed shifting function, it can be widely used for general cutting, and its two power output shafts can be used for power output at the same time, so double output torque can be obtained and the effect of balanced drive can be achieved. For precise position positioning, the backlash elimination function is activated to achieve the purpose of precise position control of the spindle. In addition, the spindle drive uses only one set of drive groups as the driving force to reduce the cost of the entire drive system.

<present invention>

(1) ‧‧‧Drive Group

(11) ‧‧‧ spur gear

(12)‧‧‧ Pipes

(13)‧‧‧Land

(2) ‧‧‧ Backlash Elimination Mechanism

(21)‧‧‧First helical gear

(211)‧‧‧ Straight teeth

(212)‧‧‧ Left oblique helical teeth

(213) ‧‧‧ actuation slots

(22)‧‧‧Second helical gear

(221)‧‧‧ Straight teeth

(222)‧‧‧Right helical teeth

(223) ‧‧‧Slots

(23)‧‧‧Power helical gears

(24)‧‧‧Power helical gears

(25) ‧‧‧Pistons

(251)‧‧‧ Pipes

(26) ‧ ‧ top sales

(261)‧‧‧Flexible parts

(27)‧‧‧ bushings

(271) ‧‧‧ channels

(28)‧‧‧ swivel joints

(3)‧‧‧Transmission

(G1)‧‧‧First shifting mechanism

(G2)‧‧‧Second shifting mechanism

(31)‧‧‧Transmission gear

(311)‧‧‧ Internal tooth

(312) ‧‧‧ outer tooth segments

(32)‧‧‧ Front transmission parts

(321)‧‧‧First external tooth

(322)‧‧‧Second external toothing

(33)‧‧‧ toothed disc

(331)‧‧‧ Inner ring tooth

(332) ‧‧‧ linkage external teeth

(34)‧‧‧ planetary gears

(35)‧‧‧ shaft seat

(36)‧‧‧Transmission gear

(361)‧‧‧Internal segment

(362)‧‧‧ outer tooth segments

(37) ‧‧ ‧ dial

(38)‧‧·Transfer piston rod

(39) ‧‧‧ Positioning Block

(391)‧‧‧ teeth

(e1)‧‧‧ Gears

(d1)‧‧‧ Gears

(4) ‧ ‧ spindle

(41)‧‧‧ Gears

<existing>

(5) ‧‧‧Drive Group

(51)‧‧‧Transmission

(52) ‧‧‧Drive shaft

(53)‧‧‧ Gears

(54)‧‧‧ Spindle

(56)‧‧‧ helical gears

(57)‧‧‧Hydraulic cylinder

(6) ‧‧‧Drive Group

(61)‧‧‧Transmission

(62)‧‧‧Main power motor

(63)‧‧‧Transmission

(64)‧‧‧Workbench

(65)‧‧‧Servomotor

First picture: schematic diagram of prior art (1)

Second picture: schematic diagram of prior art (2)

Third picture: schematic diagram of prior art (3)

Figure 4: Schematic diagram of prior art (4)

Figure 5: Schematic diagram of the overall appearance of the present invention

Figure 6: Schematic diagram of the backlash elimination mechanism of the present invention (release state)

Figure 7: A-axis and helical gear meshing diagram of the backlash eliminating mechanism of the present invention

Figure 8: Schematic diagram of the gearbox of the present invention (high speed)

Ninth diagram: Schematic diagram of the gearbox structure of the present invention (low speed)

Figure 10: Schematic diagram of the spindle drive of the present invention

Figure 11: Schematic diagram of the spindle drive of the present invention (belt drive)

Twelfth Figure: Schematic diagram of the spindle double drive transmission of the present invention

Thirteenth Figure: Meshing diagram of the double-drive transmission gear of the present invention (A, B, C axes)

Figure 14: Meshing diagram of the double-drive transmission gear of the present invention (D, E, spindle)

Figure 15: Side view of the gearbox of the present invention

Figure 16: Schematic diagram of a partial enlargement of the high speed state of the gearbox of the present invention

Figure 17: Schematic diagram of partial enlargement of the gearbox in the low speed state of the present invention

Figure 18: Schematic diagram of the meshing state of the planetary gear of the present invention

Figure 19: Schematic diagram of the transmission of the backlash eliminating mechanism of the present invention

Figure 20: Schematic diagram of eliminating backlash state of the present invention

Twenty-first picture: the invention eliminates the backlash gear meshing diagram (A, B, C axis)

Twenty-second diagram: the invention eliminates backlash gear meshing diagram (D, E, spindle)

Twenty-third figure: schematic diagram of the application mechanism of the present invention

For a more complete and clear disclosure of the technical means, the object of the invention and the effect of the present invention, the following detailed description, and the accompanying drawings,

First, please refer to the fifth to ninth figures, which provide a schematic diagram of the overall structure of the spindle driving device, which is mainly corresponding to the gearbox (3) via a driving group (1) and a backlash eliminating mechanism (2). Drive two power output shafts (E, D axis), so that the two power output shafts drive the main shaft (4) to run, among them: Please refer to the sixth and seventh figures together, the drive group (1) is equipped with a drive The A-axis (which is a plug shaft) has a straight tooth portion (11) on the surface of the drive A-axis, and a conduit (12) that is electrically connected inside.

The backlash eliminating mechanism (2) includes first and second helical gears (21) and (22) assembled on the driving A-axis straight tooth portion (11), and the first and second helical gears ( 21), (22) internal spurs (211), (221) corresponding to the driving A-axis straight tooth portion (11), and the first and second helical gears (21), (22) externally left Right oblique helical teeth (212), (222), gears with different helical directions, and fixed at the end faces by bolts, and the first helical gear (21) corresponds to the power helical gear (24) of the C-axis, and the second The helical gear (22) corresponds to a power helical gear (23) for transmitting a B-axis, and the first helical gear (21) is provided with an actuating groove (213) for correspondingly embedding a piston provided with a pipeline (251) ( 25), the second helical gear (22) is provided with a through slot (223), and a through pin (26) embedded in the elastic member (261) is disposed in the through slot (223), and the elastic One end of the piece (261) corresponds to the end surface of the first helical gear (21), and a bushing (27) which is sleeved with the piston (25) is arranged on the driving A-axis, and the bushing (27) corresponds to the piston (25). The pipeline (251) and the A-axis pipeline (12) are also provided with a passage (271), and a rotation can be set at the end of the A-axis to drive the A-axis and the piston (25) pipeline (251). Connector (28).

Please refer to the eighth to ninth and fifteenth diagrams together. The gearbox (3) contains the first and second shifting mechanisms (G1) and (G2) for the high and low gears of the main shaft (4). During shifting, the first and second shifting mechanisms (G1) and (G2) are respectively provided with power output E and D axes to synchronously receive the power transmitted by the C and B axes to drive the main shaft (4) for high and low shifting. The first and second shifting mechanisms (G1) and (G2) are mainly provided with a transmission gear (31) on the C and B shafts respectively, and an internal tooth portion (311) is arranged inside the front end of the transmission gear (31). The outer side of the rear section is provided with an outer tooth segment (312) corresponding to a front transmission member (32) provided with a first outer tooth portion (321) at a front portion, and the front transmission member (32) a second outer tooth portion (322) is disposed in the rear portion, and the unsupported toothed disc (33) is sleeved on the outer side of the continuous transmission gear (31), and the inner ring tooth portion (331) is disposed inside the toothed disc (33), and the outer portion The interlocking external tooth portion (332) is provided with at least two or more interlocking rotational speed changes between the second external tooth portion (322) of the front transmission member (32) and the inner tooth portion (331) of the toothed disc (33). Planetary gear (34), while the planetary gear (34) is pivotally set at a power output E, The D-axis coupled shaft seat (35) continues to be coupled with the gear (31) and the toothed disc (33). The outer gear portion (332) is sleeved with a shifting gear seat (36). The shifting gear base (36) The inner tooth segment (361) and the outer tooth segment (362) are respectively disposed inside and outside, and the shift gear seat (36) is combined with a linked dial block (37), and one end of the dial block (37) and a shifting piston rod (38) Knot The shifting piston rod (38) drives the shifting block (37) to drive the shifting gear base (36) and the outer gear (312) of the transmission gear (31) and the toothed disc (33) to interlock the external teeth ( 332) simultaneously engaging the high speed transmission, or disengaging the outer gear segment (312) of the transmission gear (31) and engaging the toothed disc (33) to interlock the outer tooth portion (332) to make the outer tooth segment of the shifting gear base (36) (362) The low speed transmission selection of the toothed disc (33) without the rotation of the toothed portion (391) of the positioning seat (39) provided on the machine table.

The power output E and D axes are the ones that receive the power transmitted by the C and B axes, and transmit the main shaft (4).

Please refer to the sixth, eighth to eleventh drawings together, the spindle drive device comprises a main shaft (4), two power output shafts (E, D axis), a gearbox (3), and a backlash elimination mechanism ( 2) [as shown in Figure 6] and a drive group (1), the drive group (1) can be a built-in motor (as shown in Figure 10) or an external spindle motor driven by a belt (13) As shown in the eleventh figure, when the driving group rotates, the first and second helical gears (21) and (22) respectively transmit power to the C and B axes via the power helical gears (24) and (23), respectively. Further, power is transmitted to the power output E and the D axis via the first and second shifting mechanisms (G1) and (G2), respectively, and the main shaft (4) is simultaneously driven by the power output E and the D axis.

Please refer to the sixth, tenth to fourteenth drawings together. At the beginning of the rotation of the drive group (1), the gear (e1) on the E-axis and the gear (d1) on the D-axis are simultaneously meshed with the main shaft (4). In the state of the gear (41), the main shaft (4) starts to rotate smoothly. At this time, the first and second helical gears (21) and (22) are on the axis of the A-axis due to the relationship between the left and right spirals. The position is automatically adjusted so that the gears (e1), (d1) and the gear (41) are both in meshing state, so that the function of the balanced drive can be achieved.

For the connection, please refer to the fifteenth to eighteenth figures. When the high and low speed shifting functions of the spindle are performed in the drive system, the first and second shifting mechanisms (G1) in the gearbox are used. (G2) is synchronously executed. Hereinafter, a single group shifting mechanism is used as an explanation. When the high speed is switched, the shifting piston rod (38) in the first shifting mechanism (G1) is retracted via the power input to drive the dial (37). Displacement, and its power input can be air pressure or oil pressure, and the dial block (37) drives the shift gear seat (36) to retreat the displacement, so that the inner gear segment (361) of the shift gear seat (36) and the transmission gear (31) The outer tooth portion (312) and the interlocking outer tooth portion (332) of the toothed disc (33) are engaged, so that when the power of the C-axis is transmitted, the C-axis is synchronously operated via the transmission gear (31) and the toothed disc (33). And the front transmission member (32) of the front end tooth portion (311) of the transmission gear (31) and the first outer tooth portion (321) are also synchronously operated at the same speed, and therefore, the front transmission member (32) the second external tooth The planetary gear (34) between the portion (322) and the inner ring tooth portion (331) of the toothed disc (33) transmits a shaft seat (35) that is coupled with the power output E-axis, and the power output E-axis drives the main shaft (4) to form. high speed The operator of the gear (as shown in Figure 16).

Conversely, when the low gear is switched, the shifting piston rod (38) in the first shifting mechanism (G1) is pushed forward by the power to loosen the displacement of the dial (37), and the dial (37) drives the shifting gear. The seat (36) is advanced in displacement so that the inner tooth segment (361) of the shift gear carrier (36) is disengaged from the outer tooth segment (312) of the transmission gear (31) and meshes with the outer tooth portion (332) of the toothed disc (33), and The outer gear segment (362) of the shifting gear base (36) is engaged with the toothed portion (391) of the positioning seat (39) provided on the machine table, so that the toothed disc (33) is engaged and fixed without rotating, so that when C When the power of the shaft is transmitted, the front transmission member (311) of the front end portion (311) of the transmission gear (31) and the first external tooth portion (321) are engaged (3 2) The synchronous operation, and the toothed disc (33) is fixed without being rotated, so that the planetary gear (34) is rotated by the second external tooth portion (322) of the front transmission member (32) to allow the planetary gear (34) The inner ring gear (331) of the toothed disc (33) drives the shaft base (35) to decelerate, so the above action forms a low speed, so that the power output E-axis drives the main shaft (4) to form a low-speed operation (as shown in Fig. 17). 〕; When the low-speed transmission, with the power output E, D axis has a balanced drive function and can double the torque output, reduce the size of the transmission mechanism, reduce the acceleration and deceleration time; when the main shaft (4) has high and low gear The switching function can be widely used for general cutting.

Please refer to the nineteenth to twenty-second diagrams together. When the spindle must be accurately positioned, the backlash elimination function is activated to achieve the purpose of precise position control of the spindle; and the backlash elimination function must be activated. Actuated by the oil pressure, the action is as follows: a piston (25) is arranged inside the actuating groove (213) of the first helical gear (21), and a rotary joint (28) is arranged in front of the transmission A-axis to eliminate the backlash. When the function is started, the power (oil pressure or air pressure) enters the pipeline (12) of the transmission A-axis through the rotary joint (28), and then passes through the passage (271) of the sleeve (27) to the inside of the first helical gear (21). a piston (25) pipe (251) for pushing the first and second helical gears (21), (22) to rotate forward, and a gear back that meshes between the gears (e1), (d1) and the gear (41) The gap is eliminated (as shown in Fig. 21~22); when the backlash elimination function is released, the power [oil pressure or air pressure] is released, and the second helical gear (22) is grooved (223). The inner elastic member (261) and the top pin (26) push the first and second helical gears (21) and (22) back to reset, and the backlash eliminating function is released.

Therefore, the present invention provides a spindle driving device, which is mainly provided with The spindle drive device of the high and low gear shifting and backlash elimination mechanism can drive the spindle at high speed without starting the backlash elimination function, and has high and low gear shifting functions, which can be widely used for general cutting. When the spindle is accurately positioned, the backlash elimination function is activated to achieve the purpose of precise position control of the spindle. Therefore, the spindle can be used for high- and low-speed shifting functions, and backlash elimination is required for precise position control. The machine tool spindle; the applied machinery such as the floor boring and milling machine spindle, the vertical lathe work table, the milling and lathe composite processing machine table, etc. (as shown in Figure 23).

The above is only a part of the embodiments of the present invention, and is not intended to limit the present invention. It is intended to be included in the scope of the present invention.

As described above, the composition of the component and the implementation description thereof show that the present invention has many advantages compared with the prior art, and is described as follows: the spindle drive device of the present invention has the same power for the spindle drive and the angle positioning control. Drive group [motor], which can reduce the cost of components.

The spindle driving device of the invention can automatically compensate and adjust and eliminate the backlash caused by the pitch error between the transmission gears.

The spindle drive device of the present invention and the prior art double-drive transmission design have the advantages of not occupying space.

The spindle driving device of the present invention can perform adjustment and setting of pre-pressure.

The spindle driving device of the invention has the driving design of the spindle with high and low-speed shifting switching and backlash eliminating mechanism, so that the spindle can be operated at high speed without the backlash eliminating function, and has high and low-speed shifting functions for wide range. Used in general machining; and when the main When the axis is accurately positioned, the backlash elimination function is activated to achieve the purpose of precise position control of the spindle.

According to the spindle driving device of the invention, the balanced driving function can double the torque output, reduce the size of the transmission mechanism, and reduce the acceleration and deceleration time.

In summary, the embodiments of the present invention can achieve the expected use efficiency, and the specific structure disclosed therein has not been seen in similar products, nor has it been disclosed before the application, and has completely complied with the provisions of the Patent Law. And the request, the application for the invention of a patent in accordance with the law, please forgive the review, and grant the patent, it is really sensible.

(1) ‧‧‧Drive Group

(11) ‧‧‧ spur gear

(12)‧‧‧ Pipes

(2) ‧‧‧ Backlash Elimination Mechanism

(21)‧‧‧First helical gear

(211)‧‧‧ Straight teeth

(212)‧‧‧ Left oblique helical teeth

(213) ‧‧‧ actuation slots

(22)‧‧‧Second helical gear

(221)‧‧‧ Straight teeth

(222)‧‧‧Right helical teeth

(223) ‧‧‧Slots

(23)‧‧‧Power helical gears

(24)‧‧‧Power helical gears

(25) ‧‧‧Pistons

(251)‧‧‧ Pipes

(26) ‧ ‧ top sales

(261)‧‧‧Flexible parts

(27)‧‧‧ bushings

(271) ‧‧‧ channels

(28)‧‧‧ swivel joints

Claims (5)

A spindle driving device is mainly equipped with a driving group (1) and a backlash eliminating mechanism (2) and a gearbox (3) to simultaneously correspond to the power output E and D axes, so that the power output E and the D axis drive the spindle (4) Performing the operation, wherein: the driving group (1) is provided with a driving A-axis, a spur tooth portion (11) is disposed on the surface of the driving A-axis, and a pipeline (12) through which the conduction is penetrated is provided; The backlash eliminating mechanism (2) includes first and second helical gears (21) and (22) assembled on the driving A-axis straight tooth portion (11), and the first and second helical gears (21) (22) The inner teeth (211) and (221) are respectively meshed with the driving A-axis straight tooth portion (11), and the first and second helical gears (21) and (22) are respectively left and right. The helical helical teeth (212), (222), and the first helical gear (21) corresponds to a power helical gear (24) that drives a C-axis, and the second helical gear (22) corresponds to a power helical gear that drives a B-axis. (23), the first helical gear (21) is provided with an actuating groove (213) corresponding to the piston (25) embedded with the pipe (251), and the second helical gear (22) is provided with a wearer a groove (223) having an embedded elasticity in the groove (223) a top pin (26) of the member (261), and one end of the elastic member (261) correspondingly abuts against the end surface of the first helical gear (21), and then a sleeve sleeved with the piston (25) is disposed on the driving A-axis ( 27), the bushing (27) is also provided with a passage (271) corresponding to the piston (25) pipe (251) and the A-axis pipe (12), and an input power can be set to the drive A at the end of the A-axis. a rotary joint (28) of the shaft and the piston (25) pipe (251); the gearbox (3) includes first and second shifting mechanisms (G1), (G2), When the main shaft (4) is used for high and low speed shifting, the first and second shifting mechanisms (G1) and (G2) are respectively provided with power output E and D axes to synchronously receive the power transmitted by the C and B shafts. The main shaft (4) is driven to perform high-speed and low-speed shifting operations; the power output E and D axes are for transmitting the power transmitted by the C and B axes, and transmitting the main shaft (4). The spindle drive device of claim 1, wherein the first and second shifting mechanisms (G1) and (G2) of the transmission (3) are mainly provided with transmission gears on the C and B axes, respectively. 31), an inner tooth portion (311) is disposed inside the front end of the transmission gear (31), and an outer tooth portion (312) is disposed on the outer side of the rear portion, and the inner tooth portion (311) is provided with a first outer tooth portion corresponding to a front portion ( The front transmission members (32) of the 321) are in mesh with each other, and the second outer tooth portion (322) is disposed at a rear portion of the front transmission member (32), and the non-coupling toothed disc (33) is externally sleeved by the continuous transmission gear (31). The toothed disc (33) is internally provided with an inner ring tooth portion (331), and the outer portion is provided with an interlocking external tooth portion (332), and is disposed in the second outer tooth portion (322) and the toothed disc (33) of the front transmission member (32). At least two or more planetary gears (34) having a rotational speed change are disposed between the ring gear portions (331), and the planetary gears (34) are pivotally disposed on a shaft base (35) coupled to the power output E and D axes. The transmission gear (31) and the toothed disc (33) are interlocked with the outer gear portion (332) to be provided with a shifting gear base (36). The shift gear base (36) is internally and externally provided with inner tooth segments (361). ) with the outer tooth segment (362), and the shifting gear carrier (36) combined with a linked dial ( 37), one end of the dial (37) is combined with a shifting piston rod (38), and the shifting piston rod (38) drives the shifting block (37) via the power to drive the shifting gear seat (36) and the transmission gear (31) ) outer tooth segment (3 12) a high-speed transmission that simultaneously engages the external tooth portion (332) in conjunction with the toothed disc (33), or the outer tooth segment (312) of the transmission gear (31) and the meshing toothed plate (33) to interlock the external tooth portion (332). The outer tooth segment (362) of the shifting gear base (36) and the positioning seat (39) tooth portion (391) provided on the machine table engage the low speed transmission of the toothed disc (33) without rotation. The spindle drive device of claim 1 or 2, wherein the drive A-axis is a plug shaft. The spindle drive device according to claim 1 or 2, wherein the rotary joint (28) corresponds to the power of the input drive A-axis and the piston (25) pipe (251) by using oil pressure and air pressure. The spindle drive device of claim 2, wherein the power of the shifting piston rod (38) in the gearbox (3) is hydraulic or pneumatic.