JPS582192A - Turnging gear for load treating device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a load handling device, particularly a clay/
This invention relates to an improved swing device and brake device that can be attached to devices, etc.

It is well known in the blower industry that the lifting capacity of load handling equipment such as clay/equipment can be improved by providing large diameter roller tracks for supporting booms and counterbalancing devices via rollers. This type of clay/device is e.g.
1s, 483.383 U.S. Patent No. 4.013°174
Disclosed in the issue etc. U.S. Patent No. 4.013,174
No. 5,925,101 discloses a clay/equipment equipped with a swivel device with an automatic stop device, which ensures free rotation of the upper device due to the rotational force associated with the wind force, especially when the engine is stopped.

An object of the present invention is to provide a brake device that prevents rotation of a swing device when the engine of a crane device is temporarily stopped. Q13. The purpose of this project is to improve the crane device used in No. 4. An object of the present invention is to provide a hydraulic accumulator for maintaining the hydraulic pressure of a hydraulic actuating device so that a swing pinion is engaged with a ring gear even when the engine of a crane device is stopped.
K to improve the crane device disclosed in No. 13,1 '24
be.

It is an object of the present invention to improve the crane system disclosed in U.S. Pat. No. 4,013,174 by providing a mechanical anti-swivel device to prevent the upper equipment from pivoting during extended periods of downtime.

Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
explain.

In FIG. 1, a strong lift crane load handling device such as a poom bearing device 10 is disclosed.A strong lift crane device to which the present invention can be applied is disclosed, for example, in U.S. Pat. No. 013.174.The lower device of the strong cariato crane device disclosed in U.S. Pat. ) large diameter ring device 12 and roller track 14 for bearing on the
is included.

A generally box-shaped beam with a laterally extending sleeve 16 enclosing an intermediate claim 18 and supporting a bearing plate 30 is disposed at the forward end of the poom bearing arrangement IO. Support play) 20 on top of the poom and! (none of which are shown) are each pivoted via a suitable connecting play) 88.24.

At least one pivoting device 30 is provided for pivoting the poom bearing device 10 relative to the large diameter ring device zmlc. In FIGS. 1 and 3, a ring gear 32 having an inner ring is fixed to the inner circumference of the roller raceway 14,
On the other hand, a pivot link 3 for each swing device 30 supports a drive pinion/34 which is pivotally supported so as to mesh with the lift/gear gear 32, with a poom support device 10 functioning as a frame member.
It has 3. The guide flange 36 is the roller track 9f1
Concentric VCl2 to ring gear 3mK on the inner circumference of 14
and a guide roller 38 is disposed concentrically with respect to the drive pinion 34.

The drive pinion 34 is connected to the ring gear 32 during normal turning operation.
A hydraulically actuated device 40 is provided for engaging the guide roller s8 with the guide 7 flange 36. By suitably determining the diameter of the guide roller SS with respect to the depth of the teeth of the drive pinion 34 and the ring gear 38, it is possible to adjust the degree of meshing of each tooth, and even if the third ring gear is arranged eccentrically. The backlash of the drive pinion 34 can be maintained at a constant level even if a part of the ring gear 31 is unbalanced. Therefore, the roller raceway 14 and the ring gear 5ttt are attached with bolts so that they can be easily attached to each other at the work site. The guide 7 flange 36 can also be constructed from a plurality of circular arc segments which are rigidly connected to each other. However, the guide 7 flange 36 can also be constructed from a plurality of circular arc segments, but it is not possible to precisely attach the guide 7 flange 36 to the cooperating/guya segments by, for example, welding. It is preferable to leave it there.

Since the guide row 238 allows the meshing degree of the teeth on the drive pinion 34 and the ring gear r511 to be substantially constant, it is clear that the machining accuracy of the teeth on the ring gear 32 is not required to be very high.

For this reason, it is sufficient to create the toothed portion of the ring gear by the flame torch cutting method. In FIGS. 1-3, the ring gear 32 and the guide 7 flange 36 are shown in FIGS.
Although it is fixed to the inner periphery of the a-ra track section 14, it will be obvious that it may be arranged on the outer periphery of the a-ra track section 14. In this case as well, the drive pinion 34 and the guide roller 38
are meshed with the same INK ring gear 33 and guide 7 flange 36, respectively.

First, the turning device will be explained.

To drive each drive pinion 34, a reversible hydraulic motor 42 is supported on the pivot link 33, and a pinion drive shaft 44 is connected to the output shaft 46 of the hydraulic motor 43.
iC spline connection.

Binion drive shaft 44 is pivotally supported in a bearing within housing 48 provided at the free end of pivot link r53 (see FIG. 3).

・The power source and hydraulic circuit for driving the % hydraulic motor 4a are simply shown in FIG. A set of reversible output pumps 62 whose power source is variable through transmission device No. 6
Oil is supplied from tanks 66 to reversible output pumps 62 through supply channels 5B each having a filter 60 therein.

Each reversible output pump 62 has a reversible path 64.6 that functions as a supply path and a return path connected to each hydraulic motor 4m11C.
It includes a knob 6 for adjusting the moving direction of the oil in the reversible path 64 and the amount of oil discharged into the reversible path 64, 66.

The casing of each reversible output pump 51A is the oil drain passage 68
It is connected to the tank 56 via. Said oil drain path 68
A heat exchanger 69 is inserted in the casing of each hydraulic motor 42, and the casing of each hydraulic motor 42 is connected to another oil drainage path. 0 to the tank 56, and leaked oil is returned to the tank 56 and drained.

In order to supply pressure oil to hydraulic actuation device number 0, engine +5
0 drives the constant displacement pump pump 2 via the output shaft No. 7 of the transmission 54. The pump 2 is connected to the supply path 5
The oil liquid is taken out from the tank 56 through the delivery channel 76.
via the hydraulically actuated device 40. On the other hand, safety valve 8
is connected to the %JJ path 76, so that the supply pressure of the 5 oils sent to the hydraulic actuator 40 is maintained constant during operation of the swing charge 30. In this case, the excess pressure of the oil is discharged from the safety valve 8 to the oil drain path 6a.

Each pivot link 33 is pinned to a bracket 84 fixed to the sleeve portion 16 by a pivot pin 8a. Also, one end of the hydraulic actuator 40 is connected to the housing 4B.
The ear part of the 8BK bottle is fastened. The pivot link 33 is disposed substantially tangential to the drive pinion 34 and the pitch IIK of the ring gear 3s so that the driving force passes through the torsional axis of the pivot pin 82 of the No. 8 placket. preferable. The two swivel devices 30 are the poom bearing device 10
It is supported on a pivot link 35 which is pivoted to the upper bracket 84, but also connects the other swivel gear 30 to other frame members (e.g. It is logical that it can be placed on a counterbalancing support that does not have a

Next, the free turning lateral groove will be explained.

No. 4,013,174 Kl! As shown, the upper equipment of the crane installation, especially the boom and mast, occupy a significant area and are therefore subject to wind pressure. 41
When the wind direction changes, such as during gusts, the boom support device 1
A large force is applied to the upper device including 0, and it tries to rotate along the large diameter ring device 1g)C as if it were a large windmill. This rotational force due to the wind is opposite to the force generated by the hydraulic motor 411 that causes the drive pinion 54 to rotate around the ring gear 32. In this case, the hydraulic motor 4 actually functions as a pump, and the force generated by the hydraulic motor 42 and counteracting the wind pressure depends on the pressure inside the hydraulic motor 43 and the pressure inside the reversible paths 64, 615. It will be understood that when the flow of pressurized fluid in the reversible passage 64.66 is substantially blocked, for example by the reversible output pump 5aVc connected to the engine 80 via the transmission 64, [A large back pressure is generated and applied to the ring gear 311 by the drive pinion 34, and the rotational force against the wind pressure becomes extremely large. For this reason, a large separating force is generated between each tooth of the drive pinion 34 and the blow gear 3. If this separating force is not effectively removed, a large load will be applied to some parts, resulting in damage or wear of the teeth. There is a problem that it becomes uneven and wears out rapidly.
,') , , (The illustrated embodiment of the invention includes the force generated by the wind applied to the back rolling in the reversible passage 64, 66 and to the drive pinion 34 upon shutdown of the engine 50 and the reversible output pump s. As the pressure reducing devices, bypass valves 92 that control the flow of oil sent by the reversible output pump δ2 when the pump is opened are provided in the reversible passages 64 and 66, respectively. In this manner, the back pressure in the reversible passages 64, 66 can be reduced appropriately depending on the degree of opening of the bypass valve 92.

In this manner, the force opposing the wind pressure generated on the drive pinion 34 and the separating force between the drive pinion 34 and the ring gear 32 can be greatly reduced.

When engine 50 is stopped, bypass valve 9m is automatically biased to the open position. As shown in FIG. 3, one end of the piston rod of the actuating device 98 in which the actuating device 98 biased by a spring is disposed is normally connected to the bypass valve 2 valve 9.
One end of the cylinder of the actuating device 9B is connected to the bypass valve 9 so as to bias the valve 2 to the open position.
It is connected to the - of the reversible output pump 51B through the cylinder 00, and when the reversible output pump δ2 is driven by the engine 50, pressurized liquid oil is introduced into the cylinder from the - of the reversible output pump Sta. The pressure at the cylinder end of the actuator 9B compresses the cylinder of the actuator 98, further displacing the bypass valve 9 to the closed position.

Thereby, communication is established between the reversible output pump 6g and the □hydraulic motor 42 so that the above-mentioned normal turning operation can be achieved.

While free to swivel, a meshing and pushing device is provided which uniformly engages the drive pinion 34 against the ring gear 32 when the engine 60 and the reversible power pump 5m are stopped. As a mesh maintaining device, a spring log is disposed between the poom bearing device 10 and the housing 4B of the swing device 30 (see Fig. 8), and the drive pinion 34 is held against the ring gear 32 by the spring 1o11. The guide row 23B is biased and brought into contact with the guide flange aSK.

Preferably, the spring 102 is disposed on top of the hydraulic actuator 40 and parallel to the hydraulic actuator 40 via an ear 104 of the poom bearing 10 and an ear 106 of the housing 48; (It should be noted that this installation configuration can be suitably modified to suit the installation space of the crane device to be installed, and may even be moved.) When the engine δ0 is stopped, the bypass valve 92 is opened, the forces opposing the wind pressure applied to the drive pinion 34 and the breaking forces are reduced, so that the reaction force of the spring 102 is only a fraction of the force exerted by the hydraulically actuated device 40 during normal pivoting motion. It will also be understood that it is only a few minutes.

Next, the case of preventing and fixing the turning movement will be explained.

If the free swiveling movement of the upper part of the crane device is not desirable, it is sufficient to fix the poom bearing 1 10 to the large diameter ring device 12, so that the gear segment 11
A pivoting fixing device 110 is provided that expands and contracts the snow into engagement with the teeth of the ring gear 32. According to a preferred embodiment, the pivot locking device 110 includes a reversible hydraulic motor.
-Year 114 is included. Rotating by the hydraulic motor 114! A screw device 11 extending in the axial direction of the fixing device 110
6 is rotated so that the gear segment 11 is suitably engaged with or separated from the ring gear 33. It will be understood that when the gear segment 112 and the ring gear 3s are engaged, the upper device of the crane device is fixed against rotation with respect to the large diameter ring device 11. [which can be arranged at any suitable location on the upper part of the crane installation, but in the case of the illustrated embodiment a single pivoting fixture on the poom bearing 10].
A station 110 is provided (see FIG. 1).

When driving the pivot locking device 110, oil is supplied to the inlet of the spring-centered bidirectional shuttle valve 110 via a supply channel 118 connected to the outlet of the adjustable safety valve 78. There is. When shuttle valve 1$10 is in the center or neutral position, flow in supply path 11a is blocked. Next, when the shuttle valve 180 is moved to the right side of the Sll by a suitable operating member such as the air cylinder
@ is supplied to advance the screw device 116 and engage the gear segment 112 with the ring gear 32. At this time, the oil is returned to the shuttle valve 120 from the other side of the hydraulic motor 114 via the supply path 126, and is further sent from the shuttle valve 120 to the drain path 68 via the return path 128. On the other hand, when the gear segment 113 is separated from the ring gear 32 and released, the shuttle valve 120 may be moved in the opposite direction by the air cylinder 130 on the other side. The direction is reversed, and the gear segment 112 is retracted via the screw device 116 to disconnect it from the ring gear 3g. It will be understood that when the shuttle valve 120 is moved forward or backward by 11 m, the internal spring returns the shuttle valve 120 to the neutral position and the supply path 118 is quickly closed. When it is desired to hold a load for a long period of time, it is desirable to use the rotating fixing device of the present invention.

-Finally, we will explain the brake device that temporarily stops the rotation of the upper scissor holder 7 of the crane device.

According to the present invention, *IIl fixed scissors device 1 device 0 as described above.
A stop device is provided that temporarily allows the upper device of the crane device to rotate when the engine 50 is stopped without energizing the engine. When carrying out erection or adjustment work on a suspended load or a structure to which a load is fixed, each swivel device 30 is equipped with a protective device, as shown in FIG. A brake drum 130 is provided mounted on a shaft 44 within a housing 133. A braking band 134 is arranged around the brake drum 130.

Brake band 13 to tighten the brake band against the brake drum
4 is fixed to the protective housing 132, and the other end is connected to the operating lever 136. Actuation lever 136
is connected to the piston end of the air cylinder arrangement IJ8, 139 via a suitable coupling device (not shown). The air cylinder devices 1311 and 139 are appropriately pressurized by the operator of the crane device to temporarily stop the swinging operation. Preferably, the air cylinder devices 138, 139 are equipped with an internal spring device that releases the brake band from the brake drum when the pressure is reduced.

According to another feature of the invention, a device is provided for maintaining the pressure in the hydraulically actuated device 40 during a temporary stop of the engine δ0. As mentioned above, the i-liquid is supplied from the pump 72 to the hydraulically actuated device 40 via the supply path 〒6 and the safety valve 'ye.
is being supplied to. Furthermore, the safety valve 7B and each hydraulic actuation device [4
0, a check valve 140 and a hydraulic nacumulator 142 are provided. The check valve 140 can prevent backflow of oil even when the pump 3 is stopped, and the hydraulic accumulator 142 can maintain the pressure within the hydraulic actuator 40 at a constant level. Preferably, the hydraulic accumulator 142 is equipped with a pressure maintainer filled with an inert gas such as nitrogen to prevent sudden changes in the pressure within the hydraulic accumulator 142 and maintain it constant. Pressure gauge 1 to display internal pressure
44 are provided respectively. On the other hand, the check valve 140 has
A manual bypass member can be provided to release fluid from the hydraulic accumulator 142 as needed to ensure safe operation and for repair work.

It is clear from the above description that according to the present invention, it is possible to provide a swing device for a large-load crane device rotatably supported on a large-diameter roller track.5. During normal turning operation, the guide roller 3B is in contact with the guide 7 flange 36 via the hydraulic actuator 40, so that even if the large ring gear 32 is slightly irregular, the backlash of the drive pinion 34 is kept constant. can. When engine 50 is temporarily stopped, pressure in hydraulic actuator 40 is maintained via hydraulic accumulator 142 and check valve 140. Each swing device 30 includes a reversible output pump 62
A braking device is provided to prevent rotation of the drive binioff 340 when the motor is stopped.

All gear segments for when not in use for a long time.
A mechanical rotation fixing device 110 is provided that engages the ring gear B and the ring gear B. On the other hand, when the upper device of the crane device is desired to freely rotate like a windmill under the ML force, the bypass valve 93 is automatically opened and the oil flowing through the reversible output pump 62 is shut off. Therefore, as the drive pinion 34 rotates, the reversible paths 64 and 66
This prevents the internal pressure from rising abnormally. Even when the hydraulic mechanism is stopped for a long period of time, the engagement between each drive pinion 34 and the ring gear 32 is maintained by the large compression spring 102.

[BRIEF DESCRIPTION OF THE DRAWINGS] Fig. 1 is a partial plan view of the upper device of a crane device in which the swing device of the present invention is installed, and Fig. 2 is a partial plan view of the upper part of the crane device in which the swing device of the present invention is installed.
FIG. 3 is a simplified hydraulic circuit diagram of the swing device of the present invention. 10... Poom support device, 12... Large diameter ring device. 14...Roller orbit part, 16...Sleeve part, 18...
- Intermediate frame 1.20...Support plate, 22.
24-... Connection plate, 30... Rotation drive device, 3
2...su/gugya, 33...pivot/gu, 34-.
・Drive pinion, 36...Guide flange, 3B・〒・
Guide roller, 40... Hydraulic pressure actuation device, 42...
Hydraulic motor, 44... Shaft, 4B... Housing, 46... Output shaft, δ0... Engine, s
G...Escapeable output pump, 54...Transmission section, 56...
Tank, δ8...supply section, 60...filter,
62...knob, 64.66...reversible path,
6B...Drainage path, 69...Heat exchanger, )O...Drainage path, 72...Pump, Fu4...Output shaft, ?
6... Supply path, f8... Safety valve, 82... Pivot bottle, 84-... Bracket, jE! ...Ear part, 9
2 bypass valve, ea-...actuating device, 100-...supply path, 102...c4 s 104 @ 106...
・Ear part, 11o...Swivel fixing device, Ill...Gear segment), 114...Hydraulic motor, 116...$
xxs...supply path, 120...shall valve, zms...air cylinder, 124,
126... Supply path, 128... 01 return 11r, 13
0... Air cylinder, 130'... Brake drum, 133... Protective housing, 134... Braking band,
136...Operating lever〒, 1313.139...
Air cylinder device, 140...Check valve, 142-mount hydraulic accumulator%144...Pressure gauge Patent applicant

Claims (1)

[Scope of Claims] 1. An upper device rotatably supported on a roller track of a large-diameter ring device and including a 7-ray member and a 15-member extending outward toward the adjacent roller track, and the roller track. a gear device disposed on the outer peripheral edge IIK of the ring gear and containing a ring gear; and the seven-frame member pivotally supported so that the pinion gear meshes with the ring gear, and which allows the pinion gear to approach and separate from the IJ seven gear. a guide 7 flange disposed concentrically with the ring gear and mounted on the roller track; and a guide cooperably pivoted with respect to the guide flange and supported on the frame member. a drive device including a reversible hydraulic motor that drives the pinion gear against the ring gear to rotate the upper device on the roller track;
The pinion gear is moved relative to the ring gear so as to maintain a substantially constant backlash between the pinion gear and the guide 7, independent of eccentricity of the roller track, and the guide 7 is moved relative to the guide 7 lunge. a hydraulic actuator for engaging the roller; a hydraulic pump device for pressurizing the reversible hydraulic motor during normal travel operation and for substantially constant pressurizing the hydraulic actuator; and a hydraulic accumulator device that maintains the oil in the hydraulic actuator in a pressurized state so that the pinion gear approaches the ring gear and the guide roller engages with the guide 7 lunge. Swivel device for load handling equipment. 2. A swing device for a load processing device according to claim 1, comprising a brake device connected to a pinion gear to prevent rotation of the pinion gear, and an operating device to operate the brake device. . 3. Claim 3, characterized in that the brake device includes a brake drum 2m disposed between a reversible hydraulic motor and a pinion gear, and a braking band cooperating with the brake drum. The turning a bale amount of the load processing device as described. 4. A swing device for a load handling device according to claim 1, wherein the hydraulic accumulator device includes a pressure maintenance bladder that maintains the pressure within the hydraulic accumulator device. 5. A check valve device disposed between the hydraulic pump device and the hydraulic accumulator device to prevent oil from flowing from the hydraulic accumulator device to the hydraulic pump device and from backflow. A swing device for a load handling device according to claim 1.