JPS6247795B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improved swing device and brake device that can be attached to a load handling device, particularly a crane device or the like that handles a large load.

The lifting capacity of load handling equipment such as crane equipment is
It is well known to those skilled in the art that improvements can be made by providing larger diameter roller tracks that support the boom and counterbalance via the rollers. Crane devices of this type are known, for example, in US Pat. No. 3,485,383;
It is disclosed in No. 4013174 etc. US Patent No.
No. 4013174 discloses a crane installation with a swivel device of 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 improve the crane device disclosed in US Pat. No. 4,013,174 by providing a brake device that prevents rotation of the swing device when the engine of the crane device is temporarily stopped. An object of the present invention is to provide a hydraulic accumulator that maintains the hydraulic pressure of the hydraulic actuator so that the swing pinion is engaged with the ring gear even when the engine of the crane device is stopped. There is a need to improve crane equipment.

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

Preferred embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, an upper device such as a boom support device 10 of a heavy load handling device such as a powerful lift crane is shown.
is disclosed. A powerful lift crane device to which the present invention is applicable is, for example, US Pat. No. 4,013,174
Disclosed in the issue. The lower unit of the heavy-duty lift crane device disclosed in U.S. Pat. is possessed.

At the forward end of the boom support device 10 is located a generally box-shaped beam with a laterally extending sleeve 16 that encloses an intermediate frame 18 and supports a support plate 20 . A boom and a mast (neither shown) are pivotally mounted on the support plate 20 via suitable coupling plates 22, 24, respectively.

Boom support device 10 for large diameter ring device 12
at least one swivel device 3 for rotating the
0 is set. In FIGS. 1 and 2, a ring gear 32 having an inner mesh is fixed to the inner circumference of the roller track 14, while a boom support device 10 functioning as a frame member is pivoted so as to mesh with the ring gear 32. Drive pinion 3
Pivot ring 33 for each swivel device 30 supporting 4
have. A guide flange 36 is mounted on the inner periphery of the roller track 14 concentrically with respect to the ring gear 32, and a guide roller 38 is attached to the drive pinion 3.
4 are arranged concentrically.

A hydraulically actuated device 40 is provided which engages the drive pinion 34 with the ring gear 32 and the guide roller 38 with the guide flange 36 during normal pivoting motion. By suitably sizing the diameter of the guide roller 38 with respect to the depth of the teeth of the drive pinion 34 and the ring gear 32, the degree of meshing of each tooth can be adjusted.
Even if the ring gear 32 is eccentrically arranged or the teeth of the ring gear 32 are uneven, the crush of the drive pinion 34 can be maintained almost constant. Therefore, the roller track section 1
4 and ring gear 32 may be comprised of a plurality of arcuate segments that are bolted together and rigidly connected to each other at the work site. The guide flange 36 can also consist of a plurality of circular arc segments, but is preferably fixed precisely, for example by welding, to the cooperating ring gear segment.

It will be appreciated that since the guide roller 38 allows the meshing degree of the teeth on the drive pinion 34 and the ring gear 32 to be substantially constant, the machining accuracy of the teeth on the ring gear 32 is not required to be very precise.
For this reason, it is sufficient to make the tooth portion of the ring gear by the flame torch cutting method. In FIGS. 1 to 3, the ring gear 32 and the guide flange 36 are fixed to the inner periphery of the roller raceway 14, but it is clear that they may be arranged on the outer periphery of the roller raceway 14. Probably. In this case as well, the drive pinion 34 and the guide roller 38 are similarly engaged with the ring gear 32 and the guide flange 36, respectively.

First, the turning device will be explained.

A reversible hydraulic motor 42 is mounted on the pivot link 33 and a pinion drive shaft 44 is splined to an output shaft 46 of the hydraulic motor 42 to drive each drive pinion 34 . The pinion drive shaft 44 is connected to the pivot link 3
3 (see FIG. 2).

FIG. 3 schematically shows a power source and hydraulic circuit for driving the hydraulic motor 42. As shown in FIG. Preferably, the power source includes an internal combustion engine 50 driving a set of variable displacement reversible output pumps 52 through a transmission 54 . Oil liquid is in tank 56
are supplied to the reversible output pumps 52 through supply passages 58 each having a filter 60 therein. Each reversible output pump 52 is connected to each hydraulic motor 42
It includes a knob 62 that adjusts the moving direction of the oil in reversible passages 64 and 66 that function as supply and return passages connected to the reversible passages 64 and 66, and the amount of oil discharged into the reversible passages 64 and 66. ing. Each reversible output pump 52
The casing is connected to the tank 56 via an oil drain passage 68. A heat exchanger 6 is provided in the oil drain path 68.
9 has been inserted. Furthermore, the casing of each hydraulic motor 42 is connected to the tank 5 via another oil drain passage 70.
6, and leaked oil is returned to the tank 56.

To supply pressure oil to the hydraulic actuator 40, the engine 50 drives a constant displacement pump 72 via an output shaft 74 of the transmission 54. Pump 72 removes fluid from tank 56 via supply channel 58 and transfers it to hydraulically actuated device 40 via delivery channel 76 . On the other hand, since the safety valve 78 is connected to the supply path 76, the supply pressure of the hydraulic fluid sent to the hydraulic actuator 40 is maintained constant during operation of the swing device 30. In this case, excess pressure oil is discharged from the safety valve 78 to the oil drain path 68.

In FIG. 1, each pivot link 33
It is pinned by a pivot pin 82 to a bracket 84 fixedly attached to 6. One end of the hydraulic actuator 40 is also pinned to an ear 88 of the housing 48. Preferably, the pivot link 33 is disposed substantially tangential to the pitch line of the drive pinion 34 and ring gear 32 so that the drive force passes approximately through the axis of the pivot pin 82 of the bracket 84. The two swivel devices 30 are the boom support device 10
Pivotal link 33 pivoted to upper bracket 84
However, further swivel gears 30 can be arranged on other frame members (e.g. counterbalance bearings, not shown) extending outwardly from the upper gear of the crane arrangement to the adjacent roller track 14. will be understood.

Next, the free rotation mechanism will be explained.

As disclosed in the above-mentioned US Pat. No. 4,013,174, the upper equipment of a crane installation, particularly the boom and mast, occupy a considerable area and are therefore subject to wind pressure. In particular, when the direction of the wind changes, such as during a gust, a large force is applied to the upper device including the boom support device 10, causing it to rotate along the large-diameter ring device 12 like a large windmill. This rotational force due to the wind is opposite to the force generated by the hydraulic motor 42 that causes the drive pinion 34 to rotate around the ring gear 32 . In this case, the hydraulic motor 4
It will be appreciated that 2 actually functions as a pump and is generated by the hydraulic motor 42 and that the force opposing the wind pressure depends on the pressure inside the hydraulic motor 42 and the pressure inside the reversible passages 64,66. For example, when flow of pressurized fluid in reversible passages 64, 66 is substantially blocked by reversible output pump 52 coupled to engine 50 via transmission 54, reversible passages 64, 66
An extremely large back pressure is generated within the ring gear 66, which is applied to the ring gear 32 by the drive pinion 34, and the rotational force that opposes the wind pressure becomes extremely large. For this reason, a large separating force is generated between the teeth of the drive pinion 34 and the ring gear 32, and if this separating force is not effectively removed, a large load will be applied to some of the teeth, resulting in damage to the teeth or wear. The problem is that it becomes uniform and wears out quickly.

The illustrated embodiment of the invention includes an engine 50
A pressure reducing device is provided to reduce the force generated by the back rolling in the reversible passages 64 and 66 and the wind applied to the drive pinion 34 when the reversible output pump 52 is stopped. As a pressure reducing device, a bypass valve 92 that blocks the flow of oil sent by the reversible output pump 52 when opened is connected to the reversible paths 64 and 66, respectively.
It is located in In this manner, the back pressure in the reversible paths 64 and 66 can be appropriately reduced depending on the degree of opening of the bypass valve 92.

In this way, the force acting against 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 92
is automatically biased to the open position. As shown in FIG. 3, a spring biased actuator 98 is provided. One end of the piston rod of actuator 98 is connected to bypass valve 92 to normally bias bypass valve 92 to an open position. One end of the cylinder of the actuating device 98 is connected to one end of the reversible output pump 52 via a supply path 100;
When the reversible output pump 52 is driven by the engine 50, pressurized liquid oil is introduced into the cylinder from one of the reversible output pumps 52. Actuation device 98
The pressure at the cylinder end compresses the spring of actuator 98, further displacing bypass valve 92 to the closed position. Thereby, the reversible output pump 52 and the hydraulic motor 42 are communicated with each other so that the above-mentioned normal turning operation can be achieved.

While freely rotating, when the engine 50 and the reversible output pump 52 are stopped, the ring gear 3
A mesh maintaining device is provided for uniformly meshing the drive pinion 34 with respect to the drive pinions 2 and 2. As a mesh maintaining device, a spring 102 is arranged between the boom support device 10 and the housing 48 of the swing device 30 (see FIG. 2). The drive pinion 34 is biased against the ring gear 32 by the spring 102, and the guide roller 38 is brought into contact with the guide flange 36. The spring 102 is preferably disposed above and parallel to the hydraulically actuated device 40 through an ear 104 of the boom support 10 and an ear 106 of the housing 48 . However, it will be appreciated that this spring mounting arrangement may be suitably modified and even reversed to suit the mounting space of the crane apparatus to which it is mounted.
Since the bypass valve 92 is opened when the engine 50 is stopped, the force opposing the wind pressure applied to the drive pinion 34 and the breaking force are reduced, so that the reaction force of the spring 102 is reduced during normal turning motion. It will also be appreciated that this is only a fraction of the force provided by pressure actuated device 40.

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

If free pivoting movement of the upper device of the crane device is not desirable, the boom support device 10 may be mechanically fixed to the large diameter ring device 12. For this purpose, the gear segment 112 is expanded and contracted, and the ring gear 3
Rotating fixing device 110 that meshes with and separates from the teeth of No. 2
is installed. According to a preferred embodiment, the pivot locking device 110 includes a reversible hydraulic motor 114. A screw device 116 extending in the axial direction of the swing fixing device 110 is rotated by the hydraulic motor 114 so that the gear segment 112 is connected to the ring gear 3.
2 and are suitably engaged with or separated from each other. When the gear segment 112 and the ring gear 32 are engaged, the upper device of the crane device is connected to the large diameter ring device 1.
It will be understood that it is fixed against rotation with respect to 2. On the other hand, a plurality of swivel locking devices 110 can be arranged adjacent to the large diameter ring device at suitable locations on the upper arrangement of the crane installation, although in the case of the illustrated embodiment a single swivel locking device 110 can be arranged on the boom bearing device 10. A fixing device 110 is provided (see FIG. 1).

When driving the pivot locking device 110, fluid is supplied via a supply channel 118 connected to the outlet of the adjustable safety valve 78 to the inlet of a bidirectional shuttle valve 120 centered by a spring. There is. When shuttle valve 120 is in a central or neutral position, flow in supply passage 118 is blocked. When the shuttle valve 120 is then moved to the right side in FIG. 3 by a suitable operating member, such as an air cylinder 122, fluid flows from the supply passage 118, through the shuttle valve 120, and to one side of the hydraulic motor 114 via the supply passage 124. is supplied and advances the screw device 116 to connect the gear segment 112 to the ring gear 32.
mesh against. At this time, the oil is applied to the hydraulic motor 1.
14 from the other side via the supply path 116 to the shuttle valve 1
20 and is further sent from the shuttle valve 120 to the drain path 68 via the return path 128. On the other hand, when separating and releasing the gear segment 113 from the ring gear 32, the shuttle valve 120 may be moved in the opposite direction using the air cylinder 130 on the other side. In this case, the flow direction of the oil in the supply passages 124, 126 is reversed, and the gear segment 112 is retracted via the screw device 116, and the mesh with the ring gear 32 is severed. Of course, it will be understood that when the gear segment 112 is moved forward or backward, the shuttle valve 120 is returned to the neutral position by the internal spring, thereby blocking and closing the supply passage 118. It is desirable to use the swing fixing device of the present invention when the wind load is small or when a crane device is used to hold the load for a long period of time.

Finally, a description will be given of a brake device that temporarily stops the rotation of the upper device of the crane device.
According to the invention, as described above, the pivoting fixing device 11
When the engine 50 is stopped without energizing the
A stop device is provided to temporarily prevent rotation of the upper device of the crane device. The above-mentioned temporary stopping device is desired when performing assembly or adjustment operations on suspended loads or on structures to which the loads are fixed.

As shown in FIG. 2, each swing device 30 is equipped with a brake drum 130' mounted on a shaft 44 within a protective housing 132. As shown in FIG. A brake band 134 is arranged around the brake drum 130'. One end of the brake band 134 is connected to the protective housing 1 so as to tighten the brake band against the brake drum.
32 , and the other end is connected to an actuation lever 136 . The actuation lever 136 is connected to the air cylinder device 138,1 via a suitable coupling device (not shown).
39 is connected to the piston end. The air cylinder devices 138 and 139 are appropriately pressurized by the operator of the crane device to temporarily stop the swinging operation. The air cylinder devices 138 and 139 include
Preferably, an internal spring device is provided which releases the brake band from the brake drum when the brake band is depressurized.

According to another feature of the invention, a device is provided for maintaining the pressure in the hydraulically actuated device 40 during periods of temporary stoppage of the engine 50. As mentioned above, oil flows from the pump 72 to the supply line 76 and the safety valve 78.
It is supplied to the hydraulic actuation device 40 via. Furthermore, a check valve 140 and a hydraulic accumulator 142 are arranged between the safety valve 78 and each hydraulic actuator 40. The check valve 140 prevents backflow of oil even when the pump 72 is stopped, and the hydraulic accumulator 142 prevents the hydraulic actuator 40 from flowing back.
The internal pressure can be maintained constant. Preferably, the hydraulic accumulator 142 is provided with a pressure maintenance bladder filled with an inert gas such as nitrogen to prevent sudden changes in the pressure within the hydraulic accumulator 142 and maintain it constant. Each hydraulic accumulator 14
2 is a pressure gauge 144 for displaying internal pressure.
are provided respectively. On the other hand, a manual bypass member can be attached to the check valve 140 to discharge oil from the hydraulic accumulator 142 as necessary to ensure safe operation and for repair work.

As is clear from the above description, it will be understood that according to the present invention, it is possible to provide a swing device for a heavy-duty crane device that is rotatably supported on a large-diameter roller track. During normal turning operation, the guide roller 38 is in contact with the guide flange 36 via the hydraulic actuator 40, so that the large ring gear 32
Even if the drive pinion 34 is slightly irregular, the backlash of the drive pinion 34 can be kept almost constant. When the engine 50 is temporarily stopped, the hydraulic accumulator 142
The pressure of the hydraulic actuator 40 is maintained via the check valve 140. Each swivel device 30 has a drive pinion 3 when the reversible output pump 52 is stopped.
A brake device is provided to prevent rotation of 4. For long periods of non-use, a mechanical pivot locking device 110 is provided which engages the gear segment 112 and the ring gear 32. On the other hand, if the upper part of the crane device is to be rotated freely like a windmill by receiving wind, the bypass valve 92 is automatically opened and the reversible output pump 5
Since the oil flowing through the reversible paths 64 and 66 is blocked, the pressure within the reversible paths 64 and 66 is prevented from increasing abnormally as the drive pinion 34 rotates. Large compression spring 1 even when the hydraulic system is stopped for a long time
02, each drive pinion 34 and ring gear 32
The occlusion between the two is maintained.

[Brief explanation of the drawing]

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, FIG. 2 is an enlarged sectional view taken approximately along the line 2--2 in FIG. 1, and FIG. FIG. 2 is a simplified hydraulic circuit diagram of the swing device of the present invention. 10... Boom support device, 12... Large diameter ring device, 14... Roller track section, 16... Sleeve section,
18... intermediate frame, 20... support plate,
22, 24... Connection plate, 30... Rotation drive device, 32... Ring gear, 33... Pivotal ring, 34... Drive pinion, 36... Guide flange, 38... Guide roller, 40... Liquid Pressure actuation device, 42... Hydraulic motor, 44... Shaft, 4
8...Housing, 46...Output shaft, 50
...Engine, 52...Reversible output pump, 54...
...Transmission section, 56...Tank, 58...Supply section, 6
0...Filter, 62...Knob, 64, 66...
...Reversible path, 68...Drainage path, 69...Heat exchanger,
70... Oil drain path, 72... Pump, 74... Output shaft, 76... Supply path, 78... Safety valve, 8
2... Pivot pin, 84... Bracket, 88...
Ear part, 92... Bypass valve, 98... Actuation device,
100... Supply path, 102... Spring, 104,1
06...Ear portion, 110...Swivel fixing device, 112
... Gear segment, 114 ... Hydraulic motor, 1
16...screw device, 118...supply path, 120...
... Shuttle valve, 122 ... Air cylinder, 12
4,126... Supply path, 128... Return path, 13
0... Air cylinder, 130'... Brake drum, 132... Protective housing, 134... Brake band, 136... Operating lever, 138, 139...
...Air cylinder device, 140...Check valve, 14
2...Hydraulic accumulator, 144...Pressure gauge.

Claims (1)

[Scope of Claims] 1. An upper device including a frame member rotatably supported on a roller track of a large-diameter ring device and extending outward toward the adjacent roller track, and an outer peripheral edge of the roller track. a gear device disposed on the frame member and including a ring gear; a mounting device disposed on the frame member for pivotally supporting the pinion gear so that the pinion gear meshes with the ring gear and moving the pinion gear toward and away from the ring gear; a guide flange disposed concentrically with a ring gear and mounted on the roller track; a guide roller pivotably supported on the guide flange and supported on the frame member; and an upper device on the roller track. a drive system including a reversible hydraulic motor for driving the pinion gear against the ring gear to cause the pinion gear to pivot; and a substantially constant backlash between the pinion gear and the ring gear independent of eccentricity of the roller track. a hydraulic actuator for moving the pinion gear relative to the ring gear and engaging the guide roller relative to the guide flange to maintain the rotational speed of the reversible hydraulic motor during normal swing motion; a hydraulic pump device that applies a substantially constant pressure; and a hydraulic fluid in the hydraulically actuated device to bring the pinion gear closer to the ring gear and engage the guide roller with the guide flange when the hydraulic pump device is stopped. a hydraulic accumulator device that maintains the pressurized state;
A swinging load handling device comprising a reversible hydraulic motor and a swing fixing device including a gear segment that is actuated by the reversible hydraulic motor and can engage with a ring gear when the upper device is stopped. Device. 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. The brake device according to claim 2, wherein the brake device includes a brake drum disposed between a reversible hydraulic motor and a pinion gear, and a brake band cooperating with the brake drum. Swivel device for load handling equipment. 4. The 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 patent claim comprising a check valve device disposed between a hydraulic pump device and a hydraulic accumulator device to prevent backflow of oil from the hydraulic accumulator device to the hydraulic pump device. A swing device for a load handling device according to item 1.