GB2142313A - Hydraulic circuit for crane - Google Patents

Abstract

A hydraulic circuit for a crane having a plurality of pumps (50, 52, 54) driven by an engine (56) has an unloading valve (58) connected to divert the output of at least one of the pumps (52) to the intake side whenever the power demands by the pumps exceed the power capacity of the engine. Should the hydraulic load on the engine (56) reach a point where the engine is nearing stall, pressure in pilot passage (64) increases to a point where internal relief valve (134) will shift, thus connecting the pilot passage (64) to the reservoir side of the pumps, causing the unloading valve (58) to shift to the left diverting pressure flow from the pump (52) through conduit (70) and blocking conduit (62). <IMAGE>

Description

SPECIFICATION Hydraulic circuit for crane This invention relates to hydraulic circuits for cranes, and more particularly, to such circuits for preventing stalling of the engine under severe load conditions.

The present invention provides a hydraulic circuit for a crane, especially an offshore crane, to prevent the engine from stalling when subjected to worst-case load conditions.

The crane's engine is sized, in terms of horsepower, to deliver only enough power to operate the crane under those loads normally anticipated. Operating all of the crane functions, i.e., swing, boom winch and hook winches, simultaneously, would require a large engine resulting in an economic waste under normal conditions. To protect an appropriately sized engine from stalling when subjected to overload conditions, the present invention provides a circuit which automatically diverts hydraulic power from one of the pumps being driven by the engine to the reservoir, thereby reducing the load on the engine and preventing it from stalling. In addition, a boom limit device is provided which utilizes the characteristics of the unloading circuit to prevent inadvertent movement of the boom to an angle which would cause damage to the crane.

The drawings are briefly described as follows: Figure 1 is a side elevational view of a pedestal mount crane incorporating a hydraulic circuit according to the present invention; Figure 2 is a schematic diagram of a hydraulic circuit according to the present invention; and Figure 3 is a side elevational view of the device for limiting both the raising and lowering of the boom.

Referring to Fig. 1, a pedestal mount crane, indicated generally at 10, has an upper works 1 2 swingably mounted on a pedestal 14 which may, for example, be secured to an offshore platform. The turntable between the upper works 1 2 and the pedestal 14 permits the swinging movement, i.e., rotation about a vertical axis, of the upper works 1 2 relative to the pedestal 14. A ring gear and pinion driven by a hydraulic swing motor provides the force for swinging in a convention manner.A boom 1 8 is pivotally attached to the upper works 1 2. The angular position of the boom 18 is controlled by a wire rope reeved between a multiple sheave bridle 20, which is attached to the boom tip by pendant 22, and a complementary sheave bail 24, which is pivotally attached to the top of an A-frame gantry 26, and wound on boom hoist or winch 28. The boom hoist 28 is mounted on the gantry 26 and driven by a hydraulic motor 30. An auxiliary hoist or winch 32 has a whip line or rope 34 wound thereon which extends over sheaves on a boom tip extension 36 and is secured to a hook 38. The winch 32 is also mounted on gantry 26 and is driven by a hydraulic motor 40. The main hook block 42 is supported by a wire rope 44 trained over a sheave or sheaves on the boom tip and wound on the main hoist or winch 46.The main winch 46 is also mounted on the gantry 26 and is driven by a hydraulic motor 48.

Hydraulic fluid power for these motors is provided by three pumps, 50, 52 and 54 driven by an engine 56 on the upper works 12.

Referring to Fig. 2, the engine 56 is shown schematically driving the three pumps or pump sections 50, 52 and 54 of an unloading pump with a pressure responsive unloading valve 58. The three pump sections 50, 52 and 54 and the unloading valve 58, and its associated circuitry, is commercially available as a unit, indicated by block 60. The unloading valve 58 normally remains in the position shown, in which pressure flow from the pump 52 is discharged into conduit 62. However, whenever flow is established through pilot passage 64, a pressure drop occurs across orifice 66. The force of pressure on the right side (acting to the left) of unloading valve 58 will exceed the combined force of pressure and compression spring on the left (acting to the right), causing the valve 58 to shift to the left.The shifted position of valve 58 will cause the output of pump 52 to be diverted to reservoir through conduit 70. The operation of this unloading valve in relation to the boom hoist circuit will be explained hereinafter.

The output of main pump 50 is directed through conduit 72 to a pair of open center, double acting hydraulic valves 74 and 76.

The valve 74 controls the main winch hydraulic motor 48 by selectively directing pressure to and returning fluid to reservoir through conduits 80 and 82. A spring-applied, pressure-release brake 84 with a one way ratchet holds the winch from unwinding in the absence of pressure and is connected to the conduit 82 so that the brake is released when pressure is directed by valve 74 into conduit 82 to rotate hydraulic motor 48 in a direction to unwind the rope 44 thereon. A counterbalance valve 86 in conduit 80 is also opened by pressure in conduit 82 to permit return of hydraulic fluid to the reservoir 78. The valve 74 is shifted to direct pressure to conduit 80 to rotate hydraulic motor 48 in a direction to reel in the rope 44. A check valve 88 permits pressure to bypass the counterbalance valve 86.The brake 84 need not be released to reel in rope 44 since the one way ratchet incorporated into the brake 84 only prevents unwinding of the rope 44.

Conduits 90 and 92 connect the valve 76 to the motor 40 to control the auxiliary winch 32 in a similar manner. A counterbalance valve 96 in conduit 90 and a one way, spring applied brake 94 are connected to conduit 92, which is pressurized to unwind the rope 34 from the winch 32. A check valve 98 provides a bypass for counterbalance valve 98. The operation of the valve 76 to control hydraulic motor 40 is identical to that described in connection with valve 74 and motor 48.

The swing motor 100 is controlled by swing valve 102 which receives hydraulic fluid pressure from pump 54 through conduit 104.

Conduits 106 and 108 connect the valve 102 with the motor 100 and are selectively pressurized and connected to reservoir to determine the direction of swing of the upper 1 2 relative to the pedestal 14. A pair of check valves 110 and 11 2 permit makeup fluid to be drawn into conduits 106 and 108 respectively to prevent cavitation in the motor 100.

The boom hoist valve 114 received fluid pressure through conduit 62, but only when the unloading valve 58 is in the position shown in Fig. 2. The valve 114 is connected to the boom hoist hydraulic motor 30 by conduits 116 and 118. The conduit 118 is pressurized when the boom tip is to be lowered, i.e., when the rope is to be unwound from the winch 28. Pressure in conduit 118 is directed to counterbalance valve 120 to permit return of fluid to the reservoir through conduit 11 6. Simultaneously, pressure in conduit 118, pressurizes a pawl release cylinder 1 22 to disengage a pawl holding the winch 28 and a one-way or ratcheting, pressurerelease brake 124. The boom will then be lowered.A check valve 1 26 permits pressure in conduit 11 6 to bypass the counterbalance valve 1 20. The spring-seated, check valve 128 permits the pressure flow supplied through conduit 62 to the valve 114 by pump 52 to be combined with the pressure flow from pump 50 conduit 72 whenever the pressure in conduit 62 exceeds that in conduit 72 by a predetermined pressure differential.

The main winch and auxiliary winch therefore, have a combined output of pumps 50 and 52 available at least a portion of the time for faster operation of these two winches. The check valve 1 30 and a pressure release valve 1 32 combine with an internal orifice within valve 114 to prevent cavitation and to permit regeneration upon lowering of the boom.

With the unloading valve 58 in the position shown, all functions of the machine are available for the operator. However, should the hydraulic load on the engine 56 reach a point that the engine is nearing stall, the pressure in pilot passage 64 will increase to the point that internal relief valve 1 34 will shift, connecting the pilot passage 64 to the reservoir side of the pump. Flow established through orifice 66 will create a pressure drop thereacross, thereby causing the unloading valve 58 to shift to the left. Pressure flow from the pump 52 will be diverted through conduit 70, while conduit 62 is blocked. In effect, the load imposed on the engine by pump 52 will be removed and the engine prevented from stalling.The engine will then be capable of sup- plying the maximum power called for by the main and auxiliary hydraulic motors 40 and 42, as well as the maximum power required by the swing motor 100. Stalling of the engine is thereby precluded.

A boom hoist limit valve 1 36 and an override valve 1 38 are connected in series in a conduit 140 extending from the pilot passage 64 to the reservoir 78. The limit valve 1 36 is normally shifted to block conduit 140, as shown in Fig. 2, while the override valve 1 38 is normally open. When the boom reaches the acceptable limit of its angular travel, the limit valve is mechanically shifted opening conduit 140 to permit flow to the reservoir 78. This causes a pressure drop across orifice 66. The difference in forces created on each side of the unloading valve 58 causes it to shift diverting fluid pressure from the pump 52 to the reservoir side through conduit 70 and blocking conduit 62. Operation of the boom hoist is therefore interrupted.The manual override valve 1 38 permits a reactivation of the boom hoist circuit. By moving this valve manually upward, the conduit 140 will once again be blocked stopping flow through the orifice 66, balancing the pressure forces on each side of valve 58, and permitting the spring 68 to shift the valve 58 once again to the position shown in Fig. 2.

Figure 3 shows a means of automatically actuating the boom limit valve 1 36. The valve 1 36 is mounted on a leg of the gantry 26 and includes a spool 142 which is urged outward by compression spring 144. A bell crank 146 is pivotally mounted from the gantry by means of pin 148. The upper arm 1 50 of bell crank 146 is positioned to engage the spool 142 with a tension spring 1 52 attached between the free end of arm 1 50 and the gantry. The tension spring 1 52 exerts a force to overcome the compression spring 144 and force the spool 142 to an inward position, i.e., to that position for valve 1 36 illustrated schematically in Fig. 2. The other arm 1 54 of bell crank 146 extends substantially transverse to the arm 1 50 with a roller 1 56 rotatably mounted on its free end. When the boom 1 8 is raised to a position where stresses in the boom become excessive due to its almost vertical orientation, the boom 1 8 will engage the roller 56 causing the bell crank 146 to rotate counterclockwise, as viewed in Fig. 3. The upper arm 1 50 will also rotate causing this spring 1 52 to extend and permitting the compression spring 144 to urge the spool 142 outward. With the spool outward, the valve 1 36 is shifted so that flow is established through conduit 140 with the result previously described.A flexible tension mem ber or cable 1 58 is pivotally attached to the boom by fitting 1 60 and to upper arm 1 50 by fitting 1 62. 'The cable 1 58 can transmit only tension and readily folds as the boom 18 is raised. However as the boom is lowered it unfolds so it is taut. This taut position is near the acceptable limit for lowering of the boom 1 8. As this limit is reached, the cable 1 58 will have pulled the upper arm 1 50 away from the spool 142, which again permits the valve. 1 38 to shift to a position in which flow is established through conduit 140. The single valve 1 36 is, therefore, effective to prevent an operator from inadvertently damaging the crane by exceeding the limits of the boom angle in both directions. It should be noted that that the characteristics of the unloading valve 58 in diverting the boom hoist pump 52 are effectively utilized by the present invention not only to prevent the boom from being raised and lowered beyond acceptable limits, but also to preclude the engine from being inadvertently loaded to a stall condition.

Claims (4)

1. A hydraulic circuit for a crane having an engine comprising: A plurality of pumps driven by said engine; and an unloading valve connecting to divert the output from at least one of said pumps to the intake side whenever the power demands by said pumps exceeds the power capacity of said engine.

2. The invention according to claim 1 and further comprising: orifice means for creating a pressure differential in response to flow means to shift said unloading valve to divert said output whenever a sufficient pressure differential exists; and a boom limit valve for establishing flow through said orifice in response to the boom reaching its angle limit.

3. The invention according to claim 3 and further comprising an override valve in series with said boom limit valve and manually shiftable to prevent flow through said orifice.

4. A hydraulic circuit for a crane substantially as described with reference to or as shown by the Drawings.