CN210795555U - Crane hydraulic system and crane - Google Patents
Crane hydraulic system and crane Download PDFInfo
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- CN210795555U CN210795555U CN201921628247.2U CN201921628247U CN210795555U CN 210795555 U CN210795555 U CN 210795555U CN 201921628247 U CN201921628247 U CN 201921628247U CN 210795555 U CN210795555 U CN 210795555U
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Abstract
The utility model discloses a hoist hydraulic system and hoist relates to the engineering machine tool field for optimize hoist hydraulic system. The crane hydraulic system comprises a pump, a first execution element, a second execution element, a first working valve, a second working valve, a first control valve and a second control valve. The pump is used for providing hydraulic oil; the first working valve is arranged on an oil path between the pump and the first execution element; the second working valve is arranged on an oil path between the pump and the second execution element; the first control valve is connected to the first working valve and is configured to control a valve position of the first working valve. The second control valve is connected to the second working valve and configured to control a valve position of the second working valve. According to the technical scheme, the multi-mode working state of the first executing element and the second executing element is realized, so that the performance of the hydraulic system of the crane is optimized.
Description
Technical Field
The utility model relates to an engineering machine tool field, concretely relates to hoist hydraulic system and hoist.
Background
At present, two action controls of auxiliary hoisting and expansion used on a crane are controlled and operated by a pilot handle, and pilot control oil ways of the two actions are switched by a reversing valve.
When the crane operation needs one of the actions of auxiliary hoisting or boom extension, the corresponding operation mode can be selected through the switching valve to operate; when the operation requires both the auxiliary winch and the telescopic action, only one operation can be completed first, and then the other action is switched,
the inventor finds that at least the following problems exist in the prior art: the existing hydraulic system has single operation mode and low efficiency. When the working condition is simple, the hydraulic system can meet the use requirement; when the operating mode is comparatively complicated, need vice book and flexible simultaneous action to accomplish the task in coordination, traditional mode of controlling can only make a round trip reciprocating's switching and reach the use purpose, controls complicacy, has increased and has controlled the time and make efficiency comparatively low. In addition, the reliability of the hydraulic system is low. The main valves of the winch and the telescopic system are controlled by a pilot handle, and the telescopic system can be out of work when any link of the handle and the switching valve fails through switching of the reversing valve, so that the reliability of the pilot control system of the telescopic system is low.
SUMMERY OF THE UTILITY MODEL
The utility model provides a hoist hydraulic system and hoist for optimize hoist hydraulic system.
An embodiment of the utility model provides a hoist hydraulic system, include:
a pump for providing hydraulic oil;
a first actuator;
a second actuator;
the first working valve is arranged on an oil path between the pump and the first execution element;
the second working valve is arranged on an oil path between the pump and the second execution element;
a first control valve connected to the first working valve and configured to control a valve position of the first working valve; and
a second control valve connected with the second working valve and configured to control a valve position of the second working valve.
In some embodiments, the first control valve comprises a pilot control valve.
In some embodiments, the second control valve comprises a pilot control valve.
In some embodiments, the crane hydraulic system further comprises:
and the first reversing valve is arranged on an oil path between the first control valve and the first working valve and is used for controlling the control oil to be conveyed to one of the first end of the first working valve and the first end of the second working valve so as to control the valve positions of the first working valve and the second working valve.
In some embodiments, the crane hydraulic system further comprises:
and the first shuttle valve is arranged among the first reversing valve, the second control valve and the second working valve and is used for leading oil in one of the first reversing valve and the second control valve to a second end of the second working valve.
In some embodiments, the crane hydraulic system further comprises:
and the second reversing valve is arranged on an oil path between the first control valve and the second working valve and is used for controlling the control oil to be conveyed to one of the second end of the first working valve and the second end of the second working valve so as to control the valve positions of the first working valve and the second working valve.
In some embodiments, the crane hydraulic system further comprises:
and the second shuttle valve is arranged among the second reversing valve, the second control valve and the second working valve, and the first shuttle valve is used for leading oil in one of the first reversing valve and the second control valve to a first end of the second working valve.
In some embodiments, the first actuator comprises a motor or a cylinder; and/or the second actuator comprises a motor or a cylinder.
In some embodiments, the first reversing valve comprises a two-position, four-way solenoid valve.
In some embodiments, the second reversing valve comprises a two-position, four-way solenoid valve.
The utility model discloses another embodiment provides a crane, include the utility model discloses arbitrary technical scheme provides crane hydraulic system.
The crane hydraulic system provided by the technical scheme is provided with a first control valve and a second control valve, wherein the first control valve can control one of a first execution element and a second execution element to be in a working state; the first control valve and the second control valve cooperate together to achieve that the first actuator and the second actuator are each in an operative state. According to the technical scheme, the multi-mode working state of the first executing element and the second executing element is realized, so that the performance of the hydraulic system of the crane is optimized.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without undue limitation to the invention. In the drawings:
fig. 1a is a schematic diagram illustrating a principle of a first working valve of a first actuator of a crane hydraulic system according to an embodiment of the present invention in a right position;
fig. 1b is a schematic diagram illustrating a first working valve of a first actuator of a crane hydraulic system according to an embodiment of the present invention in a left position;
fig. 2a is a schematic diagram illustrating a second working valve of a second actuator of a crane hydraulic system according to an embodiment of the present invention in a right position;
fig. 2b is a schematic diagram illustrating a second working valve of a second actuator of the crane hydraulic system according to the embodiment of the present invention in a left position;
fig. 3a is a schematic diagram illustrating a principle that a first working valve and a second working valve of a crane hydraulic system provided by an embodiment of the present invention are in a right position and a right position;
fig. 3b is a schematic diagram illustrating a principle that the first working valve and the second working valve of the crane hydraulic system according to the embodiment of the present invention are in the right position and the left position respectively;
fig. 3c is a schematic diagram illustrating the principle that the first working valve and the second working valve of the crane hydraulic system according to the embodiment of the present invention are in the left position;
fig. 3d is a schematic diagram illustrating a principle that the first working valve of the crane hydraulic system provided by the embodiment of the present invention is in the left position and the second working valve is in the right position;
fig. 4 is a schematic structural diagram of a crane according to another embodiment of the present invention;
fig. 5a is a schematic view of a situation that a crane hydraulic system provided by an embodiment of the present invention is applied to a crane;
fig. 5b is a schematic view of another situation that the crane hydraulic system provided by the embodiment of the present invention is applied to a crane.
Detailed Description
The technical solution provided by the present invention will be explained in more detail with reference to fig. 1 to 5 b.
The embodiment of the utility model provides a hoist hydraulic system, including pump 1, first executive component 2, second executive component 3, first work valve 4, second work valve 5, first control valve 6 and second control valve 7.
In the hydraulic system, an oil path is divided into two parts, wherein one part is a working oil path; the other is a pilot oil path. The working oil path is used for realizing the actions of the first actuator 2 and the second actuator 3. The pilot oil passage is used to control the valve position states of the first and second work valves 4, 5, and further, to control the operation modes of the first and second actuators 2, 3. Take the first actuator 2 as a motor and the second actuator 3 as a cylinder as an example. The pilot oil path controls the valve position state of the first working valve 4 to realize the forward rotation and the reverse rotation of the motor. The pilot oil path realizes the extension and retraction of the oil cylinder by controlling the valve position state of the second working valve 5. The content of the pilot oil passage will be described in detail later.
Referring to fig. 1a, a pump 1 is used to supply hydraulic oil. The pump 1 is specifically, for example, a variable displacement pump 1. An overflow oil path is arranged between the outlet of the pump 1 and the oil tank, and an overflow valve 12 is arranged on the overflow oil path.
The first working valve 4 is provided on an oil path between the pump 1 and the first actuator 2. The first working valve 4 is used to control the operating state of the first actuator 2. For example, the first actuator 2 is a cylinder, and the first working valve 4 is used for controlling the extension and retraction of the first actuator 2.
The second working valve 5 is provided in the oil path between the pump 1 and the second actuator 3. The second working valve 5 is used to control the operating state of the second actuator 3. For example, if the second actuator 3 is a motor, the second working valve 5 is used to control the second actuator 3 to rotate forward and backward.
The oil flow direction of the working oil way is as follows: flows out of the outlet of the pump 1 and then flows to the first and second working valves 4 and 5. The valve positions of the first working valve 4 and the second working valve 5 are controlled by a pilot oil path, and the following three working states are shared: only the first actuator 2 is operated, only the second actuator 3 is operated, and the first actuator 2 and the second actuator 3 are operated simultaneously. The various states will be described in detail later.
The first control valve 6 and the second control valve 7 are both located on the pilot oil path. Specifically, the first control valve 6 is connected to the first working valve 4, and the first control valve 6 is configured to control a valve position of the first working valve 4. The second control valve 7 is connected to the second working valve 5, and the second control valve 7 is configured to control a valve position of the second working valve 5.
The first control valve 6 comprises a pilot control valve, such as a pilot handle valve. The second control valve 7 comprises a pilot control valve, such as a foot valve, for example.
The control states of the first control valve 6 and the second control valve 7 are divided into the following two operating conditions:
the first operating mode is as follows: only the first control valve 6 is in the control state. In this state, the first control valve 6 may control the first working valve 4 to be in a certain working state, or may control the second working valve 5 to be in a certain working state. That is, in this case, the first control valve 6 controls one of the first working valve 4 and the second working valve 5 to be in the working state, but the first working valve 4 and the second working valve 5 cannot be in the working state at the same time. This enables the first actuator 2 and the second actuator 3 to operate alternatively.
The second working condition is as follows: the first control valve 6 and the second control valve 7 are both in a control state, and the first control valve 6 controls only the operating state of the first working valve 4, and the second control valve 7 controls only the operating state of the second working valve 5. This enables the first actuator 2 and the second actuator 3 to operate simultaneously.
Referring to fig. 1a, the crane hydraulic system further includes a first direction valve 8, the first direction valve 8 is disposed on an oil path between the first control valve 6 and the first working valve 4, and the first direction valve 8 is used for controlling to deliver control oil to one of the first end of the first working valve 4 and the first end of the second working valve 5, so as to control the valve positions of the first working valve 4 and the second working valve 5.
Referring to fig. 1a, the crane hydraulic system further includes a second direction valve 10, and the second direction valve 10 is disposed on an oil path between the first control valve 6 and the second working valve 5, and is configured to control delivery of a control oil to one of the second end of the first working valve 4 and the second end of the second working valve 5, so as to control the valve positions of the first working valve 4 and the second working valve 5.
The first reversing valve 8 and the first control valve 6 are matched together to realize valve position control of the first working valve 4 and the second working valve 5.
Referring to fig. 1a, the crane hydraulic system further comprises a first shuttle valve 9, the first shuttle valve 9 being arranged between the first direction valve 8, the second control valve 7 and the second work valve 5. The first shuttle valve 9 is used for leading the oil in one of the first reversing valve 8 and the second control valve 7 to the second end of the second working valve 5.
The first shuttle valve 9 realizes that the pilot oil can normally flow to the first end of the second working valve 5 to realize the valve position control of the second working valve 5 no matter the first reversing valve 8 controls the action of the second actuator 3 or the second control valve 7 controls the action of the second actuator 3.
Referring to fig. 1a, the crane hydraulic system further includes a second shuttle valve 11, the second shuttle valve 11 is disposed between the second direction valve 10, the second control valve 7 and the second working valve 5, and the first shuttle valve 9 is configured to pass oil of one of the first direction valve 8 and the second control valve 7 to the first end of the second working valve 5.
The first shuttle valve 9 realizes that the pilot oil can normally flow to the second end of the second working valve 5 to realize the valve position control of the second working valve 5 no matter the second reversing valve 10 controls the action of the second actuator 3 or the second control valve 7 controls the action of the second actuator 3.
As described above, the first actuator 2 comprises a motor or a cylinder. And/or the second actuator 3 comprises a motor or a cylinder.
In some embodiments, the first reversing valve 8 comprises a two-position, four-way solenoid valve.
In some embodiments, the second reversing valve 10 comprises a two-position, four-way solenoid valve.
The specific structure of the first control valve 6 and the second control valve 7 will be described below. As shown in fig. 1a, the first control valve 6 includes two three-way valves, i.e., a first three-way valve 61 and a second three-way valve 62. One of the first three-way valve 61 and the second three-way valve 62 is in a conduction state. The first three-way valve 61 and the second three-way valve 62 are handle valves, i.e., are in a conducting state if pressed, and are in a disconnecting state if lifted. The PX oil passage is used to supply pilot control oil to the first control valve 6.
When the first three-way valve 61 is in the on state, the pilot control oil can be supplied to the first end of the first working valve 4 or the first end of the second working valve 5.
When the second three-way valve 62 is in the on state, the pilot control oil can be supplied to the second end of the first working valve 4 or the second end of the second working valve 5.
The second control valve 7 also includes two three-way valves, i.e., a third three-way valve 71 and a fourth three-way valve 72. Either the third three-way valve 71 or the fourth three-way valve 72 is in a conducting state. The first three-way valve 61 and the second three-way valve 62 are both foot valves, i.e., are in a conducting state if depressed and are in a disconnected state if raised. The PX oil passage is used to supply pilot control oil to the second control valve 7.
When the third three-way valve 71 is in the on state, the pilot control oil can be supplied to the first end of the second working valve 5.
When the second three-way valve 62 is in the on state, the pilot control oil can be supplied to the second end of the second working valve 5.
Specific conditions are described below.
1. The auxiliary hoisting action (namely the motor works) and the oil cylinder does not stretch. In this condition, the first control valve 6 is in an operating state and the second control valve 7 is not in operation.
Firstly, selecting the working condition of the auxiliary winding, and pressing an auxiliary winding switching control button to enable the first reversing valve 8 and the second reversing valve 10 to be simultaneously in the left working position, so that the first reversing valve 8 and the second reversing valve 10 are not powered. The pilot oil enters a P port of the first control valve 6 through pressure, the first three-way valve 61 and the second three-way valve 62 of the first control valve 6 are correspondingly switched according to the requirement of the working condition of the auxiliary winch, and the pilot oil is controlled to respectively enter a pilot cavity of the first working valve 4 through the corresponding first reversing valve 8 and the corresponding second reversing valve 10 to push a valve core of the first working valve 4 to act and control the steering of the auxiliary winch motor. After the pressure oil enters the motor, the brake oil cylinder of the hoisting mechanism is pushed by the third shuttle valve 13, so that the motor rotates to drive the corresponding hoisting to rise and fall.
As shown in fig. 1a and 1 b. Fig. 1a shows the first, i.e. right end of the first working valve 4 being supplied with pilot oil, the first working valve 4 being in the right position. The first working valve 4 is specifically a three-position four-way solenoid valve. As shown in fig. 1a, the oil in the PX flows to the second three-way valve 62, then to the left of the second directional valve 10, and then to the first end of the first working valve 4, so that the first working valve 4 is in the right position.
In the situation shown in fig. 1a, the working oil flows from the pump 1 to the right of the first working valve 4 and then to the first actuator 2.
Fig. 1b shows the second end (i.e. the left end) of the first working valve 4 being supplied with pilot oil, the first working valve 4 being in the left position. The first working valve 4 is specifically a three-position four-way solenoid valve. As shown in fig. 1b, the oil in PX flows to the first three-way valve 61, then to the left position of the first directional valve 8, and then to the second end of the first working valve 4, so that the first working valve 4 is in the left position.
In the situation shown in fig. 1b, the working oil flows from the pump 1 to the left of the first working valve 4 and then to the first actuator 2.
2. The oil cylinder stretches and retracts, and the auxiliary winch does not act (namely the motor does not act). In this condition, the first control valve 6 is in an operating state and the second control valve 7 is not in operation.
Similarly, when the telescopic operation mode is selected, the control button of the second three-way valve 62 of the first control valve 6 is pressed, so that the first direction valve 8 and the second direction valve 10 are simultaneously in the right working position (the first direction valve 8 and the second direction valve 10 are both electrified). The pilot oil enters a port P of the first control valve 6, the first control valve 6 controls the pilot oil to pass through a corresponding first reversing valve 8 and a corresponding second reversing valve 10 and then pass through a first shuttle valve 9 or a second shuttle valve 11 and then respectively enter a pilot cavity of the second working valve 5 according to corresponding actions of telescopic working conditions, a valve core of the second working valve 5 is pushed to act, and the extension and retraction of the second execution element 3 (such as a telescopic oil cylinder) are controlled.
As shown in fig. 2a and 2 b. Wherein fig. 2a shows the second working valve 5 with its first (i.e. right) end fed with pilot oil, the second working valve 5 being in the right position. The second working valve 5 is specifically a three-position four-way solenoid valve. As shown in fig. 2a, the oil in the PX flows to the second three-way valve 62, then to the right of the second directional valve 10, then to the second shuttle valve 11, and then to the first end of the second working valve 5, so that the second working valve 5 is in the right position.
In the situation shown in fig. 2a, the working oil flows from the pump 1 to the right of the second working valve 5 and then to the second actuator 3.
Fig. 2b shows the second end (i.e. the left end) of the second working valve 5 being fed with pilot oil, the second working valve 5 being in the left position. The second working valve 5 is specifically a three-position four-way solenoid valve. The flow path of the pilot oil is shown in fig. 2b, and the oil in PX flows to the first three-way valve 61, then to the right of the first direction valve 8, then to the first shuttle valve 9, and then to the second end of the second working valve 5, so that the second working valve 5 is in the left position.
In the situation shown in fig. 2b, the working oil flows from the pump 1 to the left of the second working valve 5 and then to the second actuator 3.
3. The secondary roll is linked with the telescopic action. In this condition, the first control valve 6 is in an operating state, and the second control valve 7 is also in an operating state. The first control valve 6 controls the valve position of the first working valve 4, and the second control valve 7 controls the valve position of the second working valve 5.
In the telescopic linkage control scheme of the auxiliary hoist and the boom, the auxiliary hoist is controlled by a first control valve 6, and the telescopic action is controlled by a second control valve 7 (namely a foot valve). Firstly, selecting the secondary winding working condition, and pressing a switching control button of a first three-way valve 61 and a second three-way valve 62 of a first control valve 6 to enable a first reversing valve 8 and a second reversing valve 10 to be simultaneously in a left working position (the first reversing valve 8 and the second reversing valve 10 are not electrified). The pilot pressure oil is divided into two paths, one path enters the port P of the first control valve 6, and the other path enters the port P of the second control valve 7. At this time, according to the requirement of the auxiliary roll lifting working condition, the first three-way valve 61 and the second three-way valve 62 of the first control valve 6 are correspondingly switched, and the pilot oil is controlled to respectively pass through the corresponding first reversing valve 8 and the corresponding second reversing valve 10 and then flow to the pilot cavity of the first working valve 4, so that the valve core of the first working valve 4 is pushed to act, and the rotation of the auxiliary roll motor is controlled.
Meanwhile, the second control valve 7 is operated according to the lifting working condition to control the boom to stretch, pilot oil is controlled to enter one of the first shuttle valve 9 and the second shuttle valve 11 through the second control valve 7, and is selected to enter a pilot cavity of the second control valve 7 controlled to stretch through the pressure of the first shuttle valve 9 and the pressure of the second shuttle valve 11, so that the second control valve 7 is controlled to move to change the direction of a main oil path, and the boom oil cylinder is controlled to stretch and retract. Under the working condition state of the auxiliary roll, the first control valve 6 controls the auxiliary roll to rise and fall, and the second control valve 7 controls the oil cylinder to stretch and retract so as to realize the linkage of the auxiliary roll and the stretching and retracting. The control mode of the secondary coil in the linkage process is not different from that under the working condition of using the secondary coil independently.
Specifically, there are four cases, as shown in fig. 3a to 3 b. In the situation shown in fig. 3a, the second three-way valve 62 of the first control valve 6 is in an active state, i.e. the second three-way valve 62 is pressed. The fourth three-way valve 72 of the second control valve 7 is in an operating state, i.e., the fourth three-way valve 72 is depressed. The pilot oil is divided into two paths. The flow direction of the first path of pilot oil is as follows: the oil in the PX flows to the second three-way valve 62, then to the left position of the second directional valve 10, and then to the first, i.e., right, end of the first working valve 4. The flow direction of the pilot oil of the second path is as follows: the oil in the PX flows to the fourth three-way valve 72, then to the second shuttle valve 11, and then to the first, right end of the second working valve 5.
In the situation shown in fig. 3b, the second three-way valve 62 of the first control valve 6 is in an active state, i.e. the second three-way valve 62 is pressed. The fourth three-way valve 72 of the second control valve 7 is in an operating state, i.e., the fourth three-way valve 72 is depressed. The pilot oil is divided into two paths. The flow direction of the first path of pilot oil is as follows: the oil in the PX flows to the second three-way valve 62, then to the left position of the second directional valve 10, and then to the first, i.e., right, end of the first working valve 4. The flow direction of the pilot oil of the second path is as follows: the oil in the PX flows to the fourth three-way valve 72, then to the second shuttle valve 11, and then to the first, right end of the second working valve 5.
In the situation shown in fig. 3c, the first three-way valve 61 of the first control valve 6 is in an active state, i.e. the first three-way valve 61 is pressed. The third three-way valve 71 of the second control valve 7 is in an operating state, i.e., the third three-way valve 71 is depressed. The pilot oil is divided into two paths. The flow direction of the first path of pilot oil is as follows: the oil in the PX flows to the first three-way valve 61, then to the left position of the first direction valve 8, and then to the second end, i.e., the left end, of the first working valve 4. The flow direction of the pilot oil of the second path is as follows: the oil in PX flows to the third three-way valve 71, then to the first shuttle valve 9, and then to the second end, i.e., the left end, of the second working valve 5.
In the situation shown in fig. 3d, the first three-way valve 61 of the first control valve 6 is in an active state, i.e. the first three-way valve 61 is pressed. The fourth three-way valve 72 of the second control valve 7 is in an operating state, i.e., the fourth three-way valve 72 is depressed. The pilot oil is divided into two paths. The flow direction of the first path of pilot oil is as follows: the oil in the PX flows to the second three-way valve 62, then to the left position of the second directional valve 10, and then to the first, i.e., right, end of the first working valve 4. The flow direction of the pilot oil of the second path is as follows: the oil in the PX flows to the fourth three-way valve 72, then to the second shuttle valve 11, and then to the first, right end of the second working valve 5.
The crane hydraulic system provided by the technical scheme has the following technical effects: firstly, the operation is flexible and convenient. Because the second control valve 7 is added to the pilot control system to control the second actuator 3, specifically, for example, the boom extends and retracts, the extending and retracting can move simultaneously with the winding, the valve position of the first control valve 6 does not need to be switched back and forth, the control flexibility is increased, and the use is more convenient. The linkage of the extension and the winding of the suspension arm also shortens the operation time and increases the lifting operation efficiency. Secondly, the reliability is high. Because a second control valve 7 is introduced into a control system of the second actuator 3, the boom can be stretched and contracted without depending on the first control valve 6, when any one of the first control valve 6, the first reversing valve 8 and the second reversing valve 10 has a fault, the boom can be controlled by the second control valve 7, and the reliability of the telescopic function control is increased.
Another embodiment of the utility model provides a crane, it includes the crane hydraulic system that any one of the above-mentioned technical scheme provided.
In the situation shown in fig. 5a, the first actuator 2 is, for example, a motor, which is used to drive the slewing motion of the crane. The second actuator 3 has two possibilities: boom arms or auxiliary winches. The motion mode of the suspension arm is that the suspension arm extends out and retracts. The action mode of the auxiliary winch is to drop and lift the winch. The action of the suspension arm is driven by the oil cylinder, and the action of the winch is driven by the motor.
In the situation illustrated in fig. 5b, the first actuator 2 is, for example, a motor, which is used to drive the main hoisting hoist to hoist and lower. The second executing element 3 is, for example, an oil cylinder, and the oil cylinder is used for driving the arm support to swing up and down.
By the technical scheme, the linkage operation control of the telescopic action of the crane boom and the auxiliary roll lifting action is realized.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the scope of the present invention.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: it is to be understood that modifications may be made to the above-described arrangements in the embodiments or equivalents may be substituted for some of the features of the embodiments, but such modifications or substitutions do not depart from the spirit and scope of the present invention.
Claims (11)
1. A crane hydraulic system, comprising:
a pump (1) for providing hydraulic oil;
a first actuator (2);
a second actuator (3);
a first working valve (4) provided on an oil path between the pump (1) and the first actuator (2);
a second working valve (5) provided on an oil path between the pump (1) and the second actuator (3);
a first control valve (6) connected to the first working valve (4) and configured to control a valve position of the first working valve (4); and
a second control valve (7) connected to the second working valve (5) and configured to control a valve position of the second working valve (5).
2. The crane hydraulic system as claimed in claim 1, characterized in that the first control valve (6) comprises a pilot control valve.
3. The crane hydraulic system as claimed in claim 2, characterized in that the second control valve (7) comprises a pilot control valve.
4. The crane hydraulic system as claimed in claim 1, further comprising:
and the first reversing valve (8) is arranged on an oil path between the first control valve (6) and the first working valve (4) and is used for controlling the control oil to be conveyed to one of the first end of the first working valve (4) and the first end of the second working valve (5) so as to control the valve positions of the first working valve (4) and the second working valve (5).
5. The crane hydraulic system as recited in claim 4, further comprising:
the first shuttle valve (9) is arranged among the first reversing valve (8), the second control valve (7) and the second working valve (5), and the first shuttle valve (9) is used for leading oil in one of the first reversing valve (8) and the second control valve (7) to a second end of the second working valve (5).
6. The crane hydraulic system as recited in claim 5, further comprising:
and the second reversing valve (10) is arranged on an oil path between the first control valve (6) and the second working valve (5) and is used for controlling the control oil to be conveyed to one of the second end of the first working valve (4) and the second end of the second working valve (5) so as to control the valve positions of the first working valve (4) and the second working valve (5).
7. The crane hydraulic system as recited in claim 6, further comprising:
and the second shuttle valve (11) is arranged among the second reversing valve (10), the second control valve (7) and the second working valve (5), and the first shuttle valve (9) is used for introducing oil in one of the first reversing valve (8) and the second control valve (7) into the first end of the second working valve (5).
8. The crane hydraulic system according to claim 1, characterized in that the first actuator (2) comprises a motor or a cylinder; and/or the second actuator (3) comprises a motor or a cylinder.
9. Crane hydraulic system according to claim 4, characterized in that the first directional valve (8) comprises a two-position four-way solenoid valve.
10. The crane hydraulic system as claimed in claim 6, characterized in that the second directional valve (10) comprises a two-position four-way solenoid valve.
11. A crane comprising a crane hydraulic system as claimed in any one of claims 1 to 10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921628247.2U CN210795555U (en) | 2019-09-27 | 2019-09-27 | Crane hydraulic system and crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921628247.2U CN210795555U (en) | 2019-09-27 | 2019-09-27 | Crane hydraulic system and crane |
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| CN210795555U true CN210795555U (en) | 2020-06-19 |
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| CN201921628247.2U Active CN210795555U (en) | 2019-09-27 | 2019-09-27 | Crane hydraulic system and crane |
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