JP2015034069A - Winding drum device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a winding drum device having high degree of freedom in design.SOLUTION: A winding drum device DD1 having a winding drum 12 comprises: a first projection shaft 21 on one side of an axial direction; and a second projection shaft 21S on the other side of the axial direction. A drum drive device 24 is coupled to the first projection shaft 21, and a drum brake device 24S is coupled to the second projection shaft 21S. The drum brake device 24S has a second deceleration mechanism 30S and a second brake mechanism 32S. A low speed shaft of the second deceleration mechanism 30S is coupled to the second projection shaft 21S, and the second brake mechanism 32S is coupled to a high speed shaft side of the second deceleration mechanism 30S, and a motor is not coupled thereto.

Description

  The present invention relates to a winding drum device.

  Patent Document 1 discloses a winding drum device. This winding drum device is configured to wind a wire rope by winding a wire rope around the winding drum and rotating the winding drum.

  In this disclosed example, the winding drum includes first and second projecting shafts that project on both sides in the axial direction. The first and second projecting shafts are individually connected to drum drive devices having the same specifications. The rotation shafts of the motors of the respective drum driving devices are connected via pulleys and timing belts, and the motors of the drum driving devices of the respective systems are configured to rotate in synchronization.

  The winding drum is braked by a braking mechanism attached to each drum driving device.

Registered Utility Model No. 3016800 (FIG. 1, paragraph [0014])

  However, in such an apparatus for driving a single winding drum by two types of drum driving devices, it is necessary to rotate the first and second projecting shafts synchronously, and therefore, drum driving of the same specification is required. Since it is necessary to provide the device as a set, there is also a problem that the degree of freedom of design is small when designing is performed in consideration of driving force, braking force, power loss during operation, and the like.

  The present invention has been made to solve such a conventional problem, and an object of the present invention is to provide a winding drum device having a high degree of design freedom.

  The present invention is a hoisting drum device having a hoisting drum, wherein the hoisting drum has a first shaft on one side in the axial direction and a second shaft on the other side in the axial direction, and a drum driving device is connected to the first shaft. A drum braking device is connected to the second shaft, the drum braking device has a speed reduction mechanism and a braking mechanism, and a low speed shaft of the speed reduction mechanism is connected to the second shaft; The above-described problem is solved by adopting a configuration in which the brake mechanism is connected to the shaft side and the drive source is not connected.

  In the present invention, among the first and second shafts on one side and the other side in the axial direction of the winding drum, the second shaft side is used exclusively for braking. For this reason, synchronous rotation control is not required between the first shaft side and the second shaft side, and the drum braking device can be designed independently from the drum driving device side for both the speed reduction mechanism and the braking mechanism. it can. Therefore, both the drum driving device side and the drum braking device can be designed with a very high degree of freedom in consideration of necessary driving force and braking force, power loss during operation, and the like.

  According to the present invention, it is possible to obtain a hoisting drum device having a high degree of design freedom.

The whole block diagram of the hoisting drum apparatus of the crane which concerns on an example of embodiment of this invention Configuration diagram of the drum driving device portion of the winding drum device The block diagram which shows the deceleration mechanism of this drum drive device Configuration diagram of the drum braking device portion of the hoisting drum device The principal part block diagram of the drum drive part concerning the modification of the apparatus of the said winding drum The whole block diagram of the winding drum apparatus which concerns on other embodiment of this invention.

  Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

  FIG. 1 is an overall configuration diagram of a hoisting drum device for a crane according to an example of an embodiment of the present invention. The winding drum device DD1 is configured to wind a wire (or a rope: not shown) of a crane (not shown) around the winding drum 12 and rotate the winding drum 12 to rotate the wire.

  The winding drum 12 includes a first projecting shaft (first shaft) 21 on one axial side and a second projecting shaft (second shaft) 21S on the other axial side. A drum driving device 24 is connected to the first protruding shaft 21, and a drum braking device 24S is connected to the second protruding shaft 21S. The drum driving device 24 includes a motor 28 that is a driving source, a first reduction mechanism 30, and a first braking mechanism 32. The drum braking device 24S includes a second reduction mechanism 30S and a second braking mechanism 32S. However, no drive source is connected to the second reduction mechanism 30S.

  Details will be described below.

  1 to 4, the first protruding shaft 21 protrudes on one side in the axial direction of the winding drum 12, and the second protruding shaft 21 </ b> S protrudes on the other side in the axial direction of the winding drum 12. The first and second projecting shafts 21, 21 </ b> S constitute a rotating shaft of the winding drum 12. That is, the winding drum 12 rotates around the axis O1 of the first and second projecting shafts 21 and 21S.

  A drum driving device 24 is connected to the first protruding shaft 21. The drum drive device 24 drives the winding drum 12 by driving (rotating) the first protruding shaft 21. In the present embodiment, the drum driving device 24 also brakes the winding drum 12.

  In the present embodiment, only one motor 28 as a driving source for the winding drum 12 is provided in the drum driving device 24. That is, the motor 28 has a rated torque that can drive the winding drum 12 independently. In this embodiment, the motor 28 is a three-phase induction motor. However, the type of motor is not particularly limited. For example, you may employ | adopt the inverter motor etc. which were excellent in controllability. Further, the motor is not limited to a motor as long as it is a driving source capable of driving the winding drum 12.

  The first speed reduction mechanism 30 of the drum driving device 24 includes a three-stage speed reduction mechanism that includes a first parallel axis speed reduction part 40, an orthogonal speed reduction part 42, and a second parallel axis speed reduction part 44.

  The first parallel shaft speed reducing unit 40 is mainly composed of a helical pinion 46 provided at the tip of the motor shaft 28 </ b> A of the motor 28 and a helical gear 48 that meshes with the helical pinion 46. The helical gear 48 is incorporated on one end side of the first intermediate shaft 50. On the other end side of the first intermediate shaft 50, a bevel pinion 52 of the orthogonal reduction portion 42 is provided. The orthogonal reduction part 42 is mainly composed of the bevel pinion 52 and the bevel gear 54. The bevel gear 54 is incorporated in the second intermediate shaft 51. The second intermediate shaft 51 is provided with a helical pinion 56 of the second parallel shaft speed reducing portion 44. The second parallel axis reduction unit 44 is mainly composed of the helical pinion 56 and the helical gear 58.

  The helical gear 58 is incorporated in the output shaft 68. In this embodiment, the output shaft 68 is a hollow output shaft having a hollow portion 68A. The output shaft 68 is supported on the casing 60 of the drum driving device 24 by a pair of tapered roller bearings 62 and 64. The output shaft 68 is connected to the first projecting shaft 21 of the winding drum 12 through a key (not shown) in the hollow portion 68A. That is, in this embodiment, the first protruding shaft 21 is supported by the bearings (taper roller bearings 62 and 64) of the first speed reduction mechanism 30 of the drum driving device 24.

  In this embodiment, the first braking mechanism 32 of the drum driving device 24 has a capacity capable of maintaining braking and stopping of the winding drum 12 by itself. The first braking mechanism 32 includes a fixed iron core 70 and a movable iron core 72. The fixed iron core 70 has an electromagnetic coil 74 and is fixed to the casing 60. The movable iron core 72 is constantly biased toward the anti-fixed iron core by a spring 76 and is configured to be drawn toward the fixed iron core 70 by energizing the electromagnet coil 74. On the other hand, a fixing plate 82 is fixed to the casing 60 via bolts 80. A brake lining 84 is disposed between the fixed plate 82 and the movable iron core 72. The brake lining 84 can rotate with the motor shaft 28 </ b> A via a key 85. Friction members 86 are disposed on the surfaces of the brake lining 84 on the fixed plate 82 side and the movable iron core 72 side, respectively.

  Therefore, the brake lining 84 is strongly held between the movable iron core 72 and the fixed plate 82 by the urging force of the spring 76 when the friction member 86 is de-energized, and gives a braking force to the motor shaft 28A. Is possible. Further, the brake lining 84 can release the braking of the motor shaft 28A because the movable iron core 72 is pulled toward the fixed iron core 70 side (against the urging force of the spring 76) when the electromagnet coil 74 is energized. It is.

  That is, the first braking mechanism 32 of the drum driving device 24 is configured to brake the motor shaft 28A when the electromagnet coil 74 is not energized and release the braking of the motor shaft 28A when the electromagnet coil 74 is energized. It is.

  Reference numeral 66 denotes a cooling fan connected to the motor shaft 28A.

  Referring mainly to FIGS. 1, 3, and 4, a drum braking device 24S capable of braking the winding drum 12 is connected to the second protruding shaft 21S.

  The drum braking device 24S includes a second reduction mechanism 30S and a second braking mechanism 32S. The low speed shaft (output shaft) 68S of the second speed reduction mechanism 30S is connected to the second protruding shaft 21S, and the high speed shaft (axis of the helical pinion 46S) 29S side of the second speed reduction mechanism 30S is connected via the third intermediate shaft 31. The second braking mechanism 32S is connected.

  However, the drive source is not connected to the high speed shaft 29S side of the second reduction mechanism 30S. That is, the drum braking device 24S is specialized in the function of braking the winding drum 12.

  In this embodiment, the configuration of the second speed reduction mechanism 30S of the drum braking device 24S is basically the same as the configuration of the first speed reduction mechanism 30 of the drum driving device 24 already described. That is, the second reduction mechanism 30S includes the same first parallel axis reduction unit 40S, orthogonal reduction unit 42S, and second parallel axis reduction unit 44S as the first reduction mechanism 30. Therefore, the same reference numerals with S at the end are attached to corresponding parts in the drawing including FIG.

  As shown in FIG. 1, the axial arrangement of each component of the first reduction mechanism 30 and the second reduction mechanism 30S with respect to the winding drum 12 is relative to the axis perpendicular to the axial center P1 of the winding drum 12 in the axial direction. And symmetric. This is because, for example, the thrust loads applied to the casings 60 and 60S are offset by the entire apparatus by causing the thrust loads generated in the orthogonal speed reducing portion 42 to be opposite to each other. In this “symmetrical configuration”, the direction in which the first speed reduction mechanism 30 is assembled into the casing 60 with respect to the first projecting shaft 21 is reversed from the direction in which the second speed reduction mechanism 30S is assembled into the casing 60S with respect to the second projecting shaft 21S. This can be achieved simply by That is, the first reduction mechanism 30 and the second reduction mechanism 30S are the same as an article. Therefore, in the present embodiment, the reduction ratio R1 of the first reduction mechanism 30 and the reduction ratio R2 of the second reduction mechanism 30S are the same (R1 = R2). Here, the reduction ratio means the denominator R when the rotational speed on the low speed shaft side is reduced to 1 / R of the rotational speed on the high speed shaft side. That is, having the same reduction ratio means that the denominator is equal, and having a large reduction ratio means that the denominator is large (decelerated more greatly).

  As described above, the second braking mechanism 32S of the drum braking device 24S is connected to the high-speed shaft 29S of the second reduction mechanism 30S via the third intermediate shaft 31. The second braking mechanism 32S basically has the same configuration as the first braking mechanism 32. Therefore, also here, parts having similar functions will be described with the same reference numerals having S at the end.

  That is, the second braking mechanism 32S also includes a fixed iron core 70S and a movable iron core 72S. The fixed iron core 70S has an electromagnetic coil 74S and is integrated with the casing 60S. The movable iron core 72S is constantly urged toward the anti-fixed iron core by a spring (76S) (not shown), and is drawn to the fixed iron core 70S side by energizing the electromagnet coil 74S. On the other hand, a fixing plate 82S is fixed to the casing 60S via bolts 80S. A brake lining 84S in which a friction member 86S is disposed is incorporated between the fixed plate 82S and the movable iron core 72S. The brake lining 84S is strongly held between the movable iron core 72S and the fixed plate 82S by the biasing force of the spring (76S) when the electromagnet coil 74S is not energized, and exerts a braking force on the shaft 90S (and hence the second projecting shaft 21S). It can be granted. In addition, when the electromagnet coil 74S is energized, the brake lining 84S can release the braking of the shaft 90S because the movable iron core 72S is drawn toward the fixed iron core 70S.

  That is, the second braking mechanism 32S is also a braking mechanism configured to brake the second protruding shaft 21S when the electromagnet coil 74S is not energized and release the braking of the second protruding shaft 21S when the electromagnet coil 74S is energized. is there.

  The drum brake device 24S is not provided with a cooling fan.

  Next, the operation of the winding drum device DD1 will be described.

  In order to wind up the wire of the winding drum 12, the motor 28 of the drum driving device 24 is operated and the motor shaft 28A is rotated. When the hoisting is performed, the electromagnet coils 74 and 74S of the first and second braking mechanisms 32 and 32S are all energized, and the braking of all the shafts is released.

  When the motor shaft 28 </ b> A rotates, the helical pinion 46 and the helical gear 48 of the first parallel shaft reduction unit 40 of the first reduction mechanism 30 rotate, and the first parallel shaft reduction unit 40 performs first-stage deceleration. As a result, the decelerated rotation is transmitted to the bevel pinion 52 of the orthogonal reduction unit 42, and the helical pinion 56 rotates at a speed further reduced by the meshing of the bevel pinion 52 and the bevel gear 54. Since the helical pinion 56 is meshed with the helical gear 58 incorporated in the output shaft 68, the output shaft 68 eventually rotates at a rotational speed obtained by reducing the rotation of the motor shaft 28A by three steps (reduction ratio R1).

  As a result, the first projecting shaft 21 inserted into the hollow portion 68 </ b> A of the output shaft 68 and capable of rotating integrally with the output shaft 68 rotates at the same speed as the output shaft 68. As the first protruding shaft 21 is rotated and driven, the wire is wound up by the winding drum 12.

  When stopping the winding, the operation of the motor 28 is stopped. After the rotation of the motor shaft 28A is stopped, each shaft is braked by the first and second braking mechanisms 32 and 32S, and the stop is maintained.

  When the wire is rewound from the winding drum 12, the energization of the electromagnet coils 74 and 74S of the first and second braking mechanisms 32 and 32S is stopped. As a result, the hoisting drum 12 rotates in reverse due to the weight of the crane lift. Then, a braking command is applied to the first braking mechanism 32 and the second braking mechanism 32S at an appropriate position. When rewinding, a braking command for the first braking mechanism 32 or a reverse rotation command for the motor 28 may be applied together.

  When the wire of the winding drum 12 is wound or unwound, the drum braking device 24S side is in a state where the second reduction mechanism 30S is rotated along with the rotation of the second protruding shaft 21S. That is, the operation of the crane is basically performed by a driving / braking operation on the drum driving device 24 side. The braking by the second braking mechanism 32S of the drum braking device 24S functions as a so-called fail-safe so that the stop of the second protruding shaft 21S is reliably maintained. For this reason, in this embodiment, the “synchronous driving” as in Patent Document 1 is unnecessary.

  On the other hand, even for fail-safe use, it is necessary to keep the hoisting drum 12 stopped only by the second braking mechanism 32S of the drum braking device 24S in an emergency. However, the rotational torque applied to the hoisting drum 12 is very strong, and if a braking mechanism is simply installed on the second projecting shaft 21S, a large braking device is required, resulting in a significant increase in cost. A problem occurs.

  In the present embodiment, the second braking mechanism 32S is not directly incorporated into the second projecting shaft 21S, but via the second deceleration mechanism 30S (via the speed increasing mechanism as viewed from the second projecting shaft 21S). ) Since it is incorporated, the capacity of the second braking mechanism 32S can be reduced by the reduction ratio R2 of the second reduction mechanism 30S, and the second braking mechanism 32S can be further reduced in size and cost.

  In addition, such a winding drum device DD1 is required to have various characteristics depending on the application, the usage mode in the field, and the like. For example, with respect to driving and braking of the winding drum 12, there are a case where the driving performance is relatively required and a case where the braking performance is required more strongly. In addition, there is a case where the compactness of the entire apparatus is strongly required, and there is a case where power loss (fuel consumption, heat generation) during operation of the apparatus is strongly concerned. Accordingly, the optimum design of the hoisting drum device DD1 is naturally different depending on the required content.

  In this case, for example, in a device that drives a single winding drum by simultaneous driving of two driving devices as in the above-mentioned Patent Document 1, “synchronous driving” is essential. As a result, it is inevitably necessary to employ a deceleration mechanism, a braking mechanism, or the like having the same characteristics, and the degree of freedom of design for the above requirements is extremely small.

  In the present embodiment, the drum braking device 24S on the second projecting shaft 21S side basically only serves to brake the hoisting drum 12, so that it is completely independent from the drum driving device 24 on the first projecting shaft 21 side. Can be designed.

  As a design example, for example, by setting the reduction ratio r2 of the second reduction mechanism 30S of the drum braking device 24S to be larger than the reduction ratio r1 of the first reduction mechanism 30 (as in this embodiment, the same reduction ratio A relatively higher braking performance can be obtained (as compared to the case where the ratio (R1 = R2) is set). The configuration in which the reduction ratio r2 of the second reduction mechanism 30S is set to be larger than the reduction ratio r1 of the first reduction mechanism 30 reduces the capacity of the second braking mechanism 32S and further reduces the size of the second braking mechanism 32S. It is also effective when you want to reduce costs.

  On the contrary, when the reduction ratio r2 of the second reduction mechanism 30S is set smaller than the reduction ratio r1 of the first reduction mechanism 30, (the same reduction ratio (R1 = R2) as in this embodiment). As compared with the case where is set), the power loss in operation of the apparatus can be further reduced, and the operation efficiency can be further increased.

  Incidentally, when high efficiency of the drum braking device 24S and compactness of the entire device are required, the types of the speed reduction mechanisms on the drum driving device 24 side and the drum braking device 24S side are made different, and the second speed reduction mechanism. As such, it is possible to make a speed reduction structure that is more efficient than the first speed reduction mechanism, or a speed reduction structure that can be made more compact. Of course, conversely, the first speed reduction mechanism itself can be a speed reduction structure that is more efficient than the second speed reduction mechanism, or a speed reduction structure that can be made more compact.

  Returning to the description of the specific operation of the present embodiment.

  In the present embodiment, the first reduction mechanism 30 and the second reduction mechanism 30S have exactly the same configuration, thereby reducing the types of parts and reducing the total manufacturing cost and inventory cost.

  The cost is also reduced by omitting the incorporation of the cooling fan. That is, in the present embodiment, the braking by the second braking mechanism 32S of the drum braking device 24S is performed only when the crane is stopped. Therefore, there is almost no heat generation due to the sliding of the friction member 86S of the brake lining 84S. During the operation of the crane, braking by the second braking mechanism 32S is not performed, and the motor is not connected to the second reduction mechanism 30S. Therefore, the second speed reduction mechanism 30S is merely rotated around in a state close to no load. For this reason, there is little heat generation during crane operation. Therefore, in the present embodiment, the drum braking device 24S side omits the incorporation of the cooling fan, and accordingly, the cost is further reduced. However, it is not prohibited to provide a cooling fan, and a cooling fan may also be provided on the drum braking device 24S side.

  In the present embodiment, the first and second protruding shafts 21 and 21S are both supported by the tapered roller bearings 62 and 64 of the first reduction mechanism 30 or the tapered roller bearings 62S and 64S of the second reduction mechanism 30S. Has been. Therefore, it is not necessary to prepare a separate pillow block or the like to support the first projecting shaft 21 or the second projecting shaft 21S. Therefore, cost reduction can be realized also in this respect. In particular, since the second reduction mechanism 30S is an existing component, it is reasonable to support the second protruding shaft 21S using the bearing of the second reduction mechanism 30S.

  Further, in the present embodiment, orthogonal reduction portions 42 and 42S are provided in the first reduction mechanism 30 of the drum driving device 24 and also in the second reduction mechanism 30S of the drum braking device 24S. Thus, the longitudinal directions of the drum driving device 24 and the drum braking device 24S are extended in a direction perpendicular to the rotation axis O1 (rotation axis of the first and second protruding shafts 21 and 21S) O1 of the winding drum 12. The overall length of the apparatus in the axial direction of the winding drum 12 can be shortened.

  FIG. 5 shows a modification of the winding drum device DD1 shown in FIGS.

  The winding drum device DD2 according to the example of FIG. 5 is a first reduction mechanism 30 of the drum driving device 24 of FIGS. A drum driving device 105 replaced with the speed reduction mechanism 103 is provided.

  That is, in the winding drum device DD2, the motor shaft 104A of the motor 104 also serves as the input shaft 106 of the eccentric oscillating speed reduction unit 100. An eccentric body 110 is incorporated in the input shaft 106 via a key 108. The outer periphery of the eccentric body 110 is eccentric with respect to the axis O <b> 2 of the input shaft 106. An external gear 114 is incorporated on the outer periphery of the eccentric body 110 via a roller bearing 112 so as to be capable of swinging and rotating. The external gear 114 is in mesh with the internal gear 116.

  In this example, the internal teeth of the internal gear 116 are constituted by a roller member 120 that is rotatably incorporated in the support pin 118. The number of teeth of the internal gear 116 (the number of roller members 120) is slightly larger (by 1 in this example) than the number of teeth of the external gear 114.

  On the other hand, a through hole 122 is formed in the external gear 114. In this through hole 122, a through pin 124 (and a sliding promoting member 125 rotatably incorporated in the through pin 124) has a clearance that is twice as large as the eccentric amount of the eccentric body 110. It is fitted. The through pin 124 is press-fitted into a carrier flange 128 that is integrated with the output shaft 126 of the eccentric oscillating speed reduction unit 100.

  The eccentric oscillating speed reduction unit 100 has the above-described configuration, and the external gear 114 is oscillated by the rotation of the input shaft 106, and the relative rotation of the external gear 114 with respect to the internal gear 116 is allowed to pass through the pin 124. It is taken out from. Each time the input shaft 106 rotates once, the external gear 114 slowly rotates at a rotational speed corresponding to the reduction ratio Re of “one-thousand of the teeth of the external gear 114”. The rotation can be extracted from the through pin 124 and the carrier flange 128.

  In the first reduction mechanism 103 of FIG. 5, a large reduction ratio Re is obtained by the eccentric oscillating type reduction part 100. Therefore, although the output of the orthogonal speed reduction unit 102 composed of the rear stage bevel pinion 130 and the bevel gear 132 is directly transmitted to the output shaft 132 (without passing through the parallel shaft speed reduction unit), the first speed reduction mechanism 103 is used. The total reduction ratio is R3, which is larger than the reduction ratio R2 on the second reduction mechanism 30S side (R3> R2). Although not shown, the drum braking device of this embodiment is the same drum braking device 24S as the previous embodiment.

  Since the other configuration is basically the same as that of the previous embodiment shown in FIGS. 1 to 4, the same reference numerals are used, and redundant description is omitted.

  In the hoisting drum device DD2 according to FIG. 5, since the first reduction mechanism 103 has a reduction ratio R3 that is larger than the reduction ratio R2 of the second reduction mechanism 30S, the reduction ratio R2 of the second reduction mechanism 30S. The driving torque of the winding drum 12 can be further increased as compared with the configurations of FIGS. 1 to 4 in which the same reduction ratio R1 is given. In other words, to obtain the same driving torque, it can be replaced with a smaller motor.

  The eccentric oscillating speed reduction unit 100 has a large starting torque (torque when starting rotation from a stopped state), but once it starts rotating, it rotates with a relatively small power loss while having a high reduction ratio. Has the characteristic of being able to continue. For this reason, since the speed reduction ratio is larger than in the previous embodiment and the starting torque is large, the burden on the first braking mechanism 32 (see FIG. 2) of the drum driving device 24 can be further reduced. (If the braking capacity is the same, the braking characteristics can be further improved). In addition, once the rotation is started, there is a characteristic that the rotation can be continued with a relatively small power loss even though it is a high reduction ratio, so that the reduction in efficiency during operation due to the high reduction ratio R3 can be suppressed as much as possible. is made of. However, the first reduction mechanism 103 of this embodiment has a larger loss than the first reduction mechanism 30 of the previous embodiment. However, the second reduction mechanism 30S has the same configuration as that of the previous embodiment, and has a smaller loss than the first reduction mechanism 103 of the present embodiment. Thereby, the increase in the loss as the whole winding drum device DD2 is suppressed.

  Furthermore, the configuration of the second reduction mechanism 30S is the same as the configuration of the second reduction mechanism 30S of FIGS. 1 to 4, and therefore the power loss of the second reduction mechanism 30S is the same as the example of FIGS. Maintained at the same level. For this reason, it is possible to perform operation while keeping the accompanying loss small even though the driving torque of the winding drum 12 is increased.

  As described above, the driving characteristics are further improved by merely changing the configuration of the first speed reduction mechanism 103 from the configurations of FIGS. 1 to 3, and the accompanying torque is reduced despite the improved driving characteristics. The winding drum device DD2 maintained in the state can be obtained.

  FIG. 6 shows still another embodiment of the present invention.

  The drum driving device of the winding drum device DD3 shown in FIG. 6 is the same as the drum driving device 105 shown in FIG. The drum driving device 105 excluding the motor 104 is adopted as the drum braking device 105S (each component is also given a symbol S). Therefore, the reduction ratio and power loss of the first reduction mechanism 103 of the drum driving device 105 of the winding drum device DD3 in FIG. 6 are the same as the reduction ratio and power loss of the second reduction mechanism 103S of the drum braking device 105S, respectively. . Accordingly, the same or similar parts as those of the previous embodiment are designated by the same reference numerals, and redundant description is omitted.

  According to this embodiment, since both the first speed reduction mechanism 103 and the second speed reduction mechanism 103S can obtain a large reduction ratio with a small size, the drum drive is performed while keeping the overall size of the winding drum device DD3 small. The braking mechanisms 32 and 32S of both the device 105 and the drum braking device 105S can be reduced in size.

  In the above embodiment, the reduction ratios of the first reduction mechanism of the drum driving device and the second reduction mechanism of the drum braking device are the same (Examples of FIGS. 1 to 4 and 6). The example in which the reduction ratio of the first reduction mechanism is larger than the reduction ratio of the second reduction mechanism (example of FIG. 5) has been shown. However, as already described, the reduction ratio of the second reduction mechanism is the first reduction ratio. You may set so that it may become larger than the reduction ratio of a mechanism. Thereby, the brake mechanism of the drum brake device can be further reduced in size. In this case, for example, the drum drive device side may be the first reduction mechanism 30 in FIG. 1 and the drum brake device side may be the first reduction mechanism 103 in FIG. The reduction ratio may be varied by changing the number of teeth with the reduction mechanism.

  Moreover, in the said embodiment, regarding the power loss of a 1st speed reduction mechanism and a 2nd speed reduction mechanism, the example (the example of FIGS. 1-4, FIG. 6) with this power loss and the power loss of a 1st speed reduction mechanism In this example, the power loss of the second speed reduction mechanism is smaller than the power loss of the first speed reduction mechanism. It is also possible to make such a design. For example, in applications where the operating time is short and the stop maintenance characteristic is important for safety, such as a hoisting drum for raising and lowering a base plate in a multilevel parking lot, the power loss of the first reduction mechanism is less than the power loss. It is possible to obtain a more advantageous effect in terms of characteristics when the power loss of the two-speed reduction mechanism is set to be larger.

  Further, the specific configuration of the first and second reduction mechanisms and the specific configuration of the first and second reduction mechanisms are not limited to the above example. For example, the reduction mechanism is configured only by the parallel axis reduction mechanism. May be.

  In the above embodiment, the first and second projecting shafts are both configured to be supported by the bearings of the first and second speed reduction mechanisms, but only one or both are, for example, dedicated. It may be supported by a pillow box or the like.

  In the above-described embodiment, both the first shaft on one side in the axial direction of the winding drum and the second shaft on the other side in the axial direction are shafts that protrude outward from the winding drum (the first projecting shaft 24 and the second projecting shaft 24S). ) Was shown. However, one or both of the first shaft and the second shaft may be arranged inside the winding drum. In other words, a part or all of one or both of the drum driving device and the drum braking device may be disposed inside the winding drum. That is, a part or all of only the drum driving device side is arranged inside the winding drum, or a part or all of only the drum braking device side is arranged inside the winding drum, A configuration may be adopted in which part or all of both the drum driving device side and the drum braking device side are arranged inside the winding drum.

  The application of the present invention is not limited to a hoisting drum for raising and lowering a base plate of a crane or a multilevel parking lot. For example, the present invention can also be applied to a hoisting drum for raising and lowering an elevator, or a hoisting drum for a ship. Accordingly, the objects to be wound up by the winding drum device according to the present invention include wires, ropes, chains, and the like, and are not particularly limited.

DD1 ... hoisting drum device 12 ... hoisting drum 21 ... first protruding shaft (first shaft)
21S: Second protruding shaft (second shaft)
24 ... Drum drive device 24S ... Drum brake device 28 ... Motor (drive source)
DESCRIPTION OF SYMBOLS 30 ... 1st deceleration mechanism 30S ... 2nd deceleration mechanism 32 ... 1st braking mechanism 32S ... 2nd braking mechanism 62, 64 ... Tapered roller bearing 68 ... Output shaft

Claims (4)

A hoisting drum device having a hoisting drum,
The hoisting drum includes a first shaft on one side in the axial direction and a second shaft on the other side in the axial direction,
A drum driving device is coupled to the first shaft;
A drum braking device is coupled to the second shaft;
The drum braking device has a speed reduction mechanism and a braking mechanism,
A low-speed shaft of the speed reduction mechanism is connected to the second shaft;
The hoisting drum device, wherein the braking mechanism is connected to the high speed shaft side of the speed reduction mechanism, and the drive source is not connected. In claim 1,
The drum driving device also includes a speed reduction mechanism, and the speed reduction mechanism of the drum braking device has a larger speed reduction ratio than the speed reduction mechanism of the drum driving device. In claim 1 or 2,
The drum driving device also has a speed reduction mechanism, and the speed reduction mechanism of the drum braking device has a smaller power loss than the speed reduction mechanism of the drum driving device. In any one of Claims 1-3,
The winding drum device, wherein the second shaft is supported by a bearing of a speed reduction mechanism of the drum braking device.

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