CN111059087B - Power distribution hydraulic system and crane - Google Patents
Power distribution hydraulic system and crane Download PDFInfo
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- CN111059087B CN111059087B CN201911337536.1A CN201911337536A CN111059087B CN 111059087 B CN111059087 B CN 111059087B CN 201911337536 A CN201911337536 A CN 201911337536A CN 111059087 B CN111059087 B CN 111059087B
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- 230000007246 mechanism Effects 0.000 claims abstract description 61
- 238000006073 displacement reaction Methods 0.000 claims abstract description 28
- 238000004891 communication Methods 0.000 claims description 3
- 230000009471 action Effects 0.000 abstract description 15
- 239000003921 oil Substances 0.000 description 135
- 239000010720 hydraulic oil Substances 0.000 description 6
- 238000004378 air conditioning Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000004044 response Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/86—Control during or prevention of abnormal conditions
- F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
- F15B2211/8633—Pressure source supply failure
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a power distribution hydraulic system which comprises a fixed displacement pump, an overflow valve, an oil inlet way, an oil return way, at least one first load execution mechanism and a second load execution mechanism, wherein the overflow valve is arranged between the oil inlet way and the oil return way, the power distribution hydraulic system also comprises at least one power control valve, the power control valves are sequentially connected to form a load series connection oil way, each first load execution mechanism and the corresponding power control valve are connected in parallel to form a first load series connection unit, the first load series connection unit is connected with the fixed displacement pump through the oil inlet way, and the first load series connection unit is connected with the oil return way through the second load execution mechanism so as to control the power consumed by each first load execution mechanism and the second load execution mechanism. The invention also discloses a crane. The invention can control the power consumption of each load so as to ensure that the action of the loads sequenced after the loads sequenced before in the load series circuit are not influenced when the loads sequenced before fail.
Description
Technical Field
The invention relates to crane equipment, in particular to a power distribution hydraulic system, and further relates to a crane.
Background
The automobile crane is a widely used engineering machine, can travel at a high speed, has good maneuverability and strong adaptability, does not need to be provided with a power supply for self-contained power, can operate in the field, is simple and flexible to operate, and is widely applied to the fields of transportation, urban construction, fire fighting, large-scale material yards, capital construction, first aid and the like. The hydraulic lifting technology is adopted on the automobile crane, so that the automobile crane has high bearing capacity and can work under the conditions of impact, vibration and poor environment.
A hydraulic system with a load series circuit is commonly used in a hydraulic system of an automobile crane (for example, an air conditioning system and a hydraulic motor heat dissipation system are commonly connected in series for use); the hydraulic system adopting the load series circuit can reduce the use number of hydraulic pumps and has high economic value; the reduction of the hydraulic pumps can reduce the oil consumption in a standby state, thereby being beneficial to protecting the environment; the reduction of the hydraulic pump can reduce the number of hydraulic elements of the system and greatly improve the reliability of the hydraulic system.
However, at present, the following problems still exist in the hydraulic system of the load series circuit to be solved: under the condition that the driving power of the hydraulic pump is constant, the failure of the previous load in the load serial circuit causes the power required by the driving load to increase, and when the power is increased to a certain degree, the subsequent load can be abnormally operated until the operation is failed.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a power distribution hydraulic system, which can control the consumed power of each load so as to ensure that the normal operation of the loads sequenced at the back is not influenced when the loads sequenced at the front in a load series circuit have faults.
A further object of the present invention is to provide a crane that can allocate the power consumption of each load in a load series circuit.
In order to achieve the above object, a first aspect of the present invention provides a power distribution hydraulic system, which includes a fixed displacement pump, an overflow valve, an oil inlet path, an oil return path, at least one first load actuator and a second load actuator, wherein the overflow valve is disposed between the oil inlet path and the oil return path, and further includes at least one power control valve, each power control valve is sequentially connected to form a load series connection oil path, each first load actuator is connected in parallel with the corresponding power control valve to form a first load series connection unit, the first load series connection unit is connected to the fixed displacement pump via the oil inlet path, and the first load series connection unit is connected to the oil return path via the second load actuator, so as to control power consumed by each first load actuator and the second load actuator.
Preferably, the power control valve includes a first port, a second port, a third port, and a fourth port.
More preferably, the number of the first load executing mechanism and the number of the power control valves are both one, the first load executing mechanism is connected with the second oil port and the third oil port of the power control valve respectively, the first oil port of the power control valve is connected with the fixed displacement pump through the oil inlet oil path, and the fourth oil port of the power control valve is connected with the oil return oil path through the second load executing mechanism, so that the first load executing mechanism and the second load executing mechanism can be switched on by reversing the power control valves.
More preferably, each of the first load actuators is connected to the corresponding second oil port and the corresponding third oil port of the power control valve, the first oil port of the power control valve located at the front end of the load serial oil path is connected to the oil inlet path, and the fourth oil port of the power control valve located at the rear end of the load serial oil path is connected to the second load actuator.
More preferably, the second load actuator is connected to the second oil port and the third oil port of one of the power control valves respectively to form a second load series unit, each of the power control valves of the first load series unit is connected to the power control valve of the second load series unit in series, and the fourth oil port of the power control valve of the second load series unit is connected to the oil return path.
Further, the power control valve includes a main valve, a directional control valve and a constant differential pressure valve, the constant differential pressure valve is connected to the second oil port and the third oil port of the power control valve, the main valve includes a first oil port connected to the first oil port of the power control valve, a second oil port connected to the second oil port of the power control valve, and a third oil port connected to the third oil port and the fourth oil port of the power control valve, the first oil port of the main valve can be selectively communicated with the second oil port or the third oil port of the main valve to control the power consumed by the first load executing mechanism and the second load executing mechanism, and the third oil port of the power control valve is communicated with the third oil port of the main valve in a one-way manner via a first check valve, the directional control valve includes a first oil port connected to a control chamber at one end of the main valve, a second oil port connected to a control chamber at the other end of the main valve, And the third oil port is connected with the first oil port of the power control valve, and the fourth oil port is connected with the pilot oil return path so as to control the reversing of the main valve.
Furthermore, the power control valve further comprises a second check valve, and the first oil port of the power control valve is in one-way communication with the main valve through the second check valve.
Specifically, the main valve is a hydraulic control reversing valve.
Typically, the first load actuator and the second load actuator are connected to the pilot oil return passage, respectively.
Preferably, the main valve is integrated with the constant-pressure-difference valve.
More preferably, a first hydraulic cavity and a second hydraulic cavity are arranged in a valve core of the main valve, an end cover assembly and a valve core of the constant pressure differential valve are sequentially arranged in the first hydraulic cavity, a first hydraulic channel communicated with the first hydraulic cavity and a second hydraulic channel communicated with the second hydraulic cavity are arranged on the valve core of the main valve, the end cover assembly is connected with the valve core of the constant pressure differential valve through an elastic piece, and the valve core of the constant pressure differential valve is located between the first hydraulic channel and the second hydraulic channel so as to control the on-off of the first hydraulic cavity and the second hydraulic cavity.
Furthermore, the inner diameter of the first hydraulic cavity is larger than that of the second hydraulic cavity, a step structure is formed at the connecting position of the first hydraulic cavity and the second hydraulic cavity, and a valve core of the constant pressure differential valve is connected with the elastic part through a stop block.
The invention provides a crane, which comprises the power distribution hydraulic system in the technical scheme of the first aspect.
Through the technical scheme, the power control valves are correspondingly connected in parallel on at least each first load executing mechanism, the power control valves can control the maximum power consumed by the first load executing mechanisms corresponding to the loads, and can also cut off the oil way, so that the flow can not flow through part or all of the first load executing mechanisms, when the flow rate can not flow through all the first load executing mechanisms, the fixed displacement pump supplies oil to the second load executing mechanism, an overflow valve is arranged between the oil inlet path and the oil return path, the system pressure can be limited, the maximum power which can be consumed by the first load executing mechanism and the second load executing mechanism corresponding to the load can be limited by combining a power control valve, and, when some or all of the first load actuators are out of order, the flow to the corresponding first load actuators is intercepted by the power control valves, the first load executing mechanism and the second load executing mechanism can be guaranteed to work normally corresponding to the load.
Additional features and more prominent advantages of the invention will be set forth in the detailed description which follows.
Drawings
FIG. 1 is a hydraulic schematic of a load series circuit in a prior art crane hydraulic system;
FIG. 2 is a hydraulic schematic of a power distribution hydraulic system of an embodiment of the present invention;
FIG. 3 is a hydraulic schematic of a power control valve in an embodiment of the present invention;
fig. 4 is a schematic structural diagram of a main valve and a constant pressure differential valve integrated in a specific embodiment of the invention.
Description of the reference numerals
1 constant delivery pump and 2 overflow valve
3 oil inlet path and 4 oil return paths
5 first load actuator 6 second load actuator
7 first oil port of power control valve P
Second oil port of power control valve A and third oil port of power control valve B
711 first hydraulic chamber 712 second hydraulic chamber
713 endcap assembly 714 first hydraulic passage
715 second hydraulic passage 716 spring
717 first oil port of main valve of block A1
Second port of main valve A2 third port of main valve A3
First port of 72 directional control valve B1 directional control valve
Second port of B2 directional control valve and third port of B3 directional control valve
Valve core 74 first one-way valve of 731 constant pressure difference valve
75 second check valve 8 pilot oil return path
1a prior art constant displacement pump 2a prior art electromagnetic directional valve
3a prior art relief valve 4a prior art preamble load
5a Prior Art follow-up load
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present invention, are given by way of illustration and explanation only, not limitation.
Furthermore, the terms "first", "second", "third", "fourth" are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated, and therefore the features defined as "first", "second", "third", "fourth" may explicitly or implicitly include one or more of the features described.
In the description of the present invention, it should be noted that, unless explicitly stated or limited otherwise, the terms "disposed" and "connected" are to be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; either directly or indirectly through intervening media, either internally or in any combination thereof. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
First, it should be noted that, after knowing the technical idea of the hydraulic connection relationship of the present invention, it is also possible for those skilled in the art to simply replace the oil passage or the valve, etc. to achieve the function of the power distribution hydraulic system of the present invention, and this also belongs to the protection scope of the present invention. The relevant hydraulic components, such as directional control valves, relief valves, motors, hydraulic pumps, etc., are well known to those skilled in the art and are common components in existing hydraulic systems, and therefore, these hydraulic components will be described only briefly below, with the description focusing on the inventive hydraulic connection relationships of the power split hydraulic system of the present invention.
Fig. 1 shows a load series circuit in a hydraulic system of a crane in the prior art, wherein a preamble load 4a is connected in series with a subsequent load 5a, the preamble load 4a is connected with a constant displacement pump 1a in the prior art through a main oil inlet oil path, the subsequent load 5a is connected with a main oil return path, the preamble load 4a and the subsequent load 5a are respectively connected in parallel with a solenoid directional valve 2a in the prior art, and an overflow valve 3a in the prior art is arranged between the main oil inlet oil path and the main oil return path; for the technical scheme of the prior art, under the condition that the driving power of the fixed displacement pump 1a of the prior art is constant, the failure of the preorder load 4a causes the power required by the driving load to increase, and when the power is increased to a certain degree, the follow-up load 5a can be caused to act abnormally until the action fails; although the action of the fore load or the following load can be cut off by the electromagnetic directional valve 2a in the prior art, the current limit is limited to the power of the electromagnetic valve, the path of the electromagnetic valve cannot be made large, and therefore the system is only used under the condition that the flow of the system is small; that is, even if the action of the preceding load is cut off by the electromagnetic directional valve 2a of the related art, the action of the following load 5a is affected.
In general, the power distribution hydraulic system of the invention adds the power control valve 7 on the basis of a load series circuit in the crane hydraulic system in the prior art, and the power control valve 7 can limit the power consumed by the parallel loads and can also cut off the action of the parallel loads, in particular, the power control valve 7 is connected in parallel on each first load executing mechanism 5, so that the normal work of the sequenced loads is not influenced when the sequenced loads are in fault.
The following description is given of a specific embodiment of the power distribution hydraulic system of the present invention in order to better illustrate the technical idea of the present invention.
As shown in fig. 2, the power distribution hydraulic system of the basic embodiment of the present invention includes a fixed displacement pump 1, a relief valve 2, an oil inlet path 3, an oil return path 4, at least one first load actuator 5 and a second load actuator 6, the overflow valve 2 is arranged between the oil inlet path 3 and the oil return path 4, and further comprises at least one power control valve 7, the power control valves 7 are sequentially connected to form a load series connection oil path, each first load executing mechanism 5 is connected with the corresponding power control valve 7 in parallel to form a first load series connection unit, the first load series connection unit is connected with the fixed displacement pump 1 through the oil inlet path 3, and the first load serial unit is connected with the oil return path 4 through the second load executing mechanism 6, so as to be able to control the power consumed by each of the first and second load actuators 5, 6.
In the basic embodiment, the power control valves 7 are connected in sequence to form a load series oil path, each first load actuator 5 is connected in parallel with one power control valve 7, wherein the hydraulic oil flows from the fixed displacement pump 1 to the oil return path 4 in sequence, the power control valve 7 in the first sequence is connected with the fixed displacement pump 1 through the oil inlet path 3, the power control valve 7 in the last sequence is connected with the oil return path 4 through the second load actuator 6, a load series loop is formed as a whole, and the maximum power which can be consumed by the load corresponding to the first load actuator 5 can be limited through the power control valve 7; an overflow valve 2 is arranged between the oil inlet path 3 and the oil return path 4, the overflow valve 2 limits the highest pressure of the system, and the maximum power which can be consumed by the load corresponding to the second load executing mechanism 6 can be limited by combining the action of a power control valve 7 and the overflow valve 2, so that to a certain extent, when the load corresponding to part or all of the first load executing mechanisms 5 fails, the consumed power is limited, and the action of the rest of the loads corresponding to the first load executing mechanisms 5 and the second load executing mechanisms 6 cannot be influenced; further, the operation of the parallel loads can be shut off by the power control valve 7, and the operation of the remaining loads may not be affected.
The first load actuator 5 and the second load actuator 6 may be hydraulic motors, can be used to drive corresponding loads, and may correspond to different loads, for example, the first load actuator 5 corresponds to an air conditioning system, and the second load actuator 6 corresponds to a hydraulic motor heat dissipation system; each first load executing mechanism 5 is connected with a power control valve 7 in parallel, and the second load executing mechanism 6 can be connected with one power control valve 7 in parallel or not connected with the power control valve 7 in parallel; thus, the maximum power that can be consumed by each load is limited by the power control valve 7; that is, when a load corresponding to a part of the first load actuator 5 fails, the power consumed by the part of the load is limited, cannot be continuously increased, and does not affect the operation of other loads; furthermore, in the power distribution hydraulic system of the present invention, the hydraulic oil flows from the fixed displacement pump 1 to the return oil passage 4 in sequence, the flow rate output by the fixed displacement pump 1 flows through each power control valve 7 in sequence, and the corresponding load can be divided into a preceding load and a subsequent load, where the preceding load and the subsequent load are opposite.
The power control valve 7 includes a first port P, a second port a, a third port B, and a fourth port C.
Further, referring to fig. 3, the power control valve 7 includes a main valve 71, a directional control valve 72 and a constant differential pressure valve 73, the constant differential pressure valve 73 is connected to the second oil port a and the third oil port B of the power control valve 7, respectively, and when the first load actuator 5 or the second load actuator 6 is connected to the power control valve 7, the constant differential pressure valve 73 is also connected to the second oil port a and the third oil port B of the power control valve 7, respectively, so that the constant differential pressure valve 73 can limit the pressure difference between the two ends of the first load actuator 5 or the second load actuator 6, thereby limiting the maximum power consumed by the load corresponding to the first load actuator 5 or the second load actuator 6; the main valve 71 includes a first port a1, a second port a2 and a third port A3, the first port a1 of the main valve 71 is connected to the first port P of the power control valve 7, the second port a2 of the main valve 71 is connected to the second port a of the power control valve 7, the third port A3 of the main valve 71 is connected to the third port B and the fourth port C of the power control valve 7, and the third port B of the power control valve 7 is in forward communication with the third port A3 of the main valve 71 through the first check valve 74, so that when the first port 1 of the main valve 71 is communicated with the third port A3 thereof, hydraulic oil does not flow to the third port B of the power control valve 7, and a certain protection effect is provided, the first port a1 of the main valve 71 can be selectively communicated with the second port a2 or the third port A3 thereof, and whether the first load actuator 5 or the second load actuator 6 is connected in series in the oil circuit can be controlled, an action to cut off the failed load; the direction control valve 72 includes a first port B1, a second port B2, a third port B3, and a fourth port B4, the first port B1 of the direction control valve 72 is connected to the one-end control chamber of the main valve 71, the second port B2 of the direction control valve 72 is connected to the other-end control chamber of the main valve 71, the third port B3 of the direction control valve 72 is connected to the first port P of the power control valve 7, the fourth port B4 of the direction control valve 72 is connected to the pilot oil return path 8, and the spool of the main valve 71 is controlled by the direction control valve 72 to move to control the direction change of the main valve 71.
Wherein, the direction control valve 72 can be an electromagnetic directional valve; the main valve 71 is a pilot operated directional valve, and as is well known, in the same case, for example, the volume is equal, the solenoid directional valve is limited by power, and the path of the solenoid directional valve cannot be large, however, the pilot operated directional valve can have a larger path than the solenoid directional valve; therefore, the power control valve 7 can be applied to the condition of large system flow, and the normal work of each load in the load series oil circuit is ensured.
Further, a second check valve 75 may be provided between the first port P of the power control valve 7 and the first port a1 of the main valve 71, and the second check valve 75 may prevent a reverse flow by allowing the first port P of the power control valve 7 to be in a forward direction and the first port a1 of the main valve 71 to be in a forward direction. A connection point of the third port B3 of the directional control valve 72 and the first port P of the power control valve 7 may be provided on an oil path between the first port P of the power control valve 7 and the second check valve 75. The first load actuator 5 and the second load actuator 6 are also connected to the pilot oil return passage 8.
For ease of understanding, the description will first be made with reference to a specific embodiment with a first load actuator 5 and a power control valve 7.
Referring to fig. 2, a first load actuator 5 is connected to a second oil port a and a third oil port B of a power control valve 7, a first oil port P of the power control valve 7 is connected to a fixed displacement pump 1 via an oil inlet path 3, a fourth oil port C of the power control valve 7 is connected to an oil return path 4 via a second load actuator 6, and the first load actuator 5 and the second load actuator 6 can be controlled to be switched on and off by reversing the power control valve 7; when the first load executing mechanism 5 and the second load executing mechanism 6 are conducted in series, the flow output by the fixed displacement pump 1 can be input through the first oil port P of the power control valve 7 and then sequentially passes through the first load executing mechanism 5 and the second load executing mechanism 6 to drive the corresponding loads to act, so that the load corresponding to the first load executing mechanism 5 can be called a first-order load, the load corresponding to the second load executing mechanism 6 can be called a subsequent load, and the power control valve 7 can control the maximum power which can be consumed by the first load executing mechanism 5, so that when the first-order load fails, the action of the subsequent load is not influenced; when the first load actuator 5 and the second load actuator 6 are interrupted, the flow output from the fixed displacement pump 1 flows directly to the second load actuator 6 through the power control valve 7 to drive the corresponding load.
Further, the number of the first load actuators 5 and the power control valves 7 is not limited to one, and more first load actuators 5 and power control valves 7 may be provided according to design requirements; specifically, each first load actuator 5 is connected to the second port a and the third port B of the corresponding power control valve 7, the power control valve 7 located at the front end of the load series oil path, that is, the first port P of the power control valve 7 with the top of the sequence is connected to the oil inlet path 3, the power control valve 7 located at the rear end of the load series oil path, that is, the fourth port C of the power control valve 7 with the last of the sequence is connected to the second load actuator 6, and for the remaining power control valves 7, for two adjacent power control valves 7, the fourth port C of one power control valve 7 is connected to the first port P of the other power control valve 7, so as to form a series oil path; in this way, when some of the loads corresponding to the first load actuators 5 fail, the maximum power that can be consumed by these loads can be limited by the power control valve 7, and even the actions of these loads can be cut off, so as to ensure that the rest of the loads act normally.
In addition, the second load actuator 6 may also be connected to a power control valve 7; specifically, the second load actuator 6 may be connected to the second oil port a and the third oil port B of one power control valve 7 respectively to form a second load series unit, the power control valve 7 of the second load series unit is connected in series to each power control valve 7 of the first load series unit, that is, the first oil port P of the power control valve 7 of the second load series unit is connected to the fourth oil port C of the adjacent power control valve 7, and the fourth oil port C of the power control valve 7 of the second load series unit is connected to the oil return path 4; in this way, the loads corresponding to the first load actuator 5 and the second load actuator 6 are controlled by the corresponding power control valves 7, and it is possible to limit the maximum power that can be consumed by the failed load or to perform an operation of shutting off the failed load.
As can be seen from the above, the power distribution hydraulic system of the present invention can individually limit the maximum power consumption of each load by the power control valve 7 in combination with the relief valve 2.
In order to make the system have a fast response speed, the constant pressure differential valve 73 may be integrated on the main valve 71.
Specifically, referring to fig. 4, a first hydraulic chamber 711 and a second hydraulic chamber 712 are arranged in a valve core of a main valve 71, an end cap assembly 713 and a valve core 731 of a constant pressure differential valve 73 are sequentially arranged in the first hydraulic chamber 711, a first hydraulic passage 714 and a second hydraulic passage 715 are further arranged on the valve core of the main valve 71, the first hydraulic passage 714 is communicated with the first hydraulic chamber 711, the second hydraulic passage 715 is communicated with the second hydraulic chamber 712, the end cap assembly 713 is connected with the valve core 731 of the constant pressure differential valve 73 through an elastic member 716, the valve core 731 of the constant pressure differential valve 73 is located between the first hydraulic passage 714 and the second hydraulic passage 715, and the valve core 731 of the constant pressure differential valve 73 can control the first hydraulic passage 714 and the second hydraulic passage 715 to be opened and closed under the action of the elastic member 716, that is, the first hydraulic chamber 711 and the second hydraulic chamber 712 can be controlled to be opened and closed; that is, the maximum differential pressure of the constant differential pressure valve 73 is defined by the elastic member 716; typically, the elastic member 716 employs a spring. The hydraulic chamber of the main valve 71 is divided into three chambers, which are respectively communicated with the fourth port C, the first port P, and the second port a of the power control valve 7, and the first hydraulic passage 714 and the second hydraulic passage 715 can be respectively connected with the fourth port C and the first port P of the power control valve 7, so as to achieve the unloading function of the constant differential pressure valve 73.
Further, the inner diameter of the first hydraulic chamber 711 is larger than the inner diameter of the second hydraulic chamber 712, a step structure is formed at a connection position of the first hydraulic chamber 711 and the second hydraulic chamber 712, the valve element 731 of the constant pressure differential valve 73 is connected with the elastic member 716 through the stopper 717, and under the action of the elastic member 716, the valve element 731 of the constant pressure differential valve 73 can block a through hole of the step structure, that is, the first hydraulic chamber 711 is blocked from being communicated with the second hydraulic chamber 712.
Of course, the inner diameter of the first hydraulic chamber 711 may be the same as the inner diameter of the second hydraulic chamber 712, and the spool 731 of the constant pressure differential valve 73 may slide in the first hydraulic chamber 711 by using the principle of a spool valve to block the first hydraulic passage 714 or the second hydraulic passage 715, thereby controlling the opening and closing of the first hydraulic chamber 711 and the second hydraulic chamber 712.
Referring to fig. 2 to 4, the power distribution hydraulic system according to the preferred embodiment of the present invention includes a fixed displacement pump 1, an overflow valve 2, an oil inlet path 3, an oil return path 4, at least one first load actuator 5, a second load actuator 6, and at least one power control valve 7, where the overflow valve 2 is disposed between the oil inlet path 3 and the oil return path 4, and each first load actuator 5 is connected to a second port a and a third port B of the corresponding power control valve 7, respectively; the second load executing mechanism 6 may be connected to the second oil port a and the third oil port B of the corresponding power control valve 7, so that, in two adjacent power control valves 7, the fourth oil port C of one power control valve 7 is connected to the first oil port P of the other power control valve 7, and according to the sequence that hydraulic oil flows from the fixed displacement pump 1 to the oil return path 4, the first oil port P of the power control valve 7 located at the foremost end is connected to the fixed displacement pump 1 through the oil inlet path 3, and the fourth oil port C of the power control valve 7 located at the rearmost end is connected to the oil return path 4; or, the second load executing mechanism 6 is not connected in parallel with the power control valve 7, and the fourth oil port C of the power control valve 7 located at the rearmost end passes through the second load executing mechanism 6 and the oil return path 4; the power control valve 7 comprises a main valve 71, a directional control valve 72, a constant pressure difference valve 73, a first check valve 74 and a second check valve 75, the constant pressure difference valve 73 is respectively connected with a second oil port A and a third oil port B of the power control valve 7, the constant pressure difference valve 73 can limit the pressure difference between two ends of the first load execution mechanism 5 or the second load execution mechanism 6, and the overflow valve 2 limits the highest pressure of the system, so that the maximum power which can be consumed by the loads corresponding to the first load execution mechanism 5 and the second load execution mechanism 6 can be controlled; the first port a1 of the main valve 71 is connected to the first port P of the power control valve 7, the second port a2 of the main valve 71 is connected to the second port a of the power control valve 7, the third port A3 of the main valve 71 is connected to the third port B and the fourth port C of the power control valve 7, and the third port B of the power control valve 7 is positively connected to the third port A3 of the main valve 71 through the first check valve 74, so as to ensure that when the system is communicated with the first port a1 of the main valve 71 and the third port A3 thereof, the hydraulic oil does not flow to the third port B of the power control valve 7, and plays a certain role of protection, the first port a1 of the main valve 71 can selectively communicate with the second port a2 or the third port A3 thereof, the main valve 71 is a pilot operated directional control valve, and as is well known, in the same case, compared with an electromagnetic directional valve, the hydraulic control directional valve can have a larger drift diameter and can be used under the condition of larger system flow; the first port B1 of the directional control valve 72 is connected to the control chamber at one end of the main valve 71, the second port B2 of the directional control valve 72 is connected to the control chamber at the other end of the main valve 71, the third port B3 of the directional control valve 72 is connected to the first port P of the power control valve 7, the fourth port B4 of the directional control valve 72 is connected to the pilot oil return path 8, and the valve body of the main valve 71 is controlled by the directional control valve 72 to move to control the reversing of the main valve 71; the first port P of the power control valve 7 is communicated with the first port a1 of the main valve 71 in a forward direction through the second check valve 75, and the second check valve 75 ensures that when the fourth port C of the power control valve 7 is connected to the return oil path, the control oil path can have enough pilot pressure to push the spool of the main valve 71, so as to ensure the realization of the spool switching action of the main valve 71.
As can be seen from the above preferred embodiment, the power control valve 7 can control the power of each load to ensure the realization of the actions of the loads in the load series oil circuit that are sequenced later, and the maximum power that each load can consume is limited by the power control valve 7, so as to quota the power and finally optimize the working state of the whole system; the main valve 71 adopts a pilot-operated directional valve, and can have a larger drift diameter compared with a solenoid directional valve, and is used under the condition of larger system flow.
For the sake of easy understanding, the operation of the power distribution hydraulic system of the present invention will be described by taking as an example the solution with a first load actuator 5 and a power control valve 7, as shown in fig. 2 and 3:
when the loads corresponding to the first load executing mechanism 5 and the second load executing mechanism 6 act simultaneously, the directional control valve 72 is powered on to push the main valve 71 to reverse, and hydraulic oil output by the fixed displacement pump 1 flows to the second load executing mechanism 6 through the first oil port P of the power control valve 7, the second oil port a of the power control valve 7, the first load executing mechanism 5, the third oil port B of the power control valve 7 and the fourth oil port C of the power control valve 7, and simultaneously drives the two loads to act; wherein, the constant pressure difference valve 73 is connected with the first load executing mechanism 5 in parallel, and limits the maximum power which can be consumed by the first load executing mechanism 5 corresponding to the load; the overflow valve 2 sets pressure to limit the maximum power output by the fixed displacement pump 1, and at the moment, the overflow valve and the fixed displacement pump jointly determine the maximum power output by the load corresponding to the second load executing mechanism 6;
when the load corresponding to the second load executing mechanism 6 acts alone, the control valve 72 is powered on, the main valve 71 is not reversed, the pressure oil output by the fixed displacement pump 1 flows to the second load executing mechanism 6 through the first oil port P and the fourth oil port C of the power control valve 7, and the load corresponding to the second load executing mechanism 6 is driven to act alone; the load pressure is limited by the set pressure of the overflow valve 2, and when the output flow of the metering pump 1 is constant, the maximum power consumption of the load corresponding to the second load actuator 6 is limited.
The crane provided by the invention comprises the power distribution hydraulic system in any one of the technical schemes, so that the crane at least has all the advantages brought by the technical scheme of the embodiment of the power distribution hydraulic system.
The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited thereto. Within the scope of the technical idea of the invention, numerous simple modifications can be made to the technical solution of the invention, including combinations of the individual specific technical features in any suitable way. The invention is not described in detail in order to avoid unnecessary repetition. Such simple modifications and combinations should be considered within the scope of the present disclosure as well.
Claims (11)
1. A power distribution hydraulic system comprises a fixed displacement pump (1), an overflow valve (2), an oil inlet oil way (3), an oil return oil way (4) and at least one first load execution mechanism (5), wherein the overflow valve (2) is arranged between the oil inlet oil way (3) and the oil return oil way (4), and is characterized by further comprising a second load execution mechanism (6) and at least one power control valve (7), each power control valve (7) is sequentially connected to form a load series oil way, each first load execution mechanism (5) is connected with the corresponding power control valve (7) in parallel to form a first load series unit, the first load series unit is connected with the fixed displacement pump (1) through the oil inlet oil way (3), and the first load series unit is connected with the oil return oil way (4) through the second load execution mechanism (6), to be able to control the power consumed by each of said first load actuator (5) and said second load actuator (6);
the power control valve (7) comprises a first oil port (P), a second oil port (A), a third oil port (B) and a fourth oil port (C);
the power control valve (7) comprises a main valve (71), a directional control valve (72) and a constant differential pressure valve (73), the constant differential pressure valve (73) is respectively connected with a second oil port (A) and a third oil port (B) of the power control valve (7), the main valve (71) comprises a first oil port (A1) connected with a first oil port (P) of the power control valve (7), a second oil port (A2) connected with a second oil port (A) of the power control valve (7) and a third oil port (A3) connected with a third oil port (B) and a fourth oil port (C) of the power control valve (7), the first oil port (A1) of the main valve (71) can be selectively communicated with the second oil port (A2) or the third oil port (A3) of the main valve to control power consumed by the first load execution mechanism (5) and the second load execution mechanism (6), and the third oil port (B) of the power control valve (7) is communicated with the first one-way valve (74) through the first oil port (B) (71) The third oil port (a 3) is in one-way conduction, the direction control valve (72) comprises a first oil port (B1) connected with one end control cavity of the main valve (71), a second oil port (B2) connected with the other end control cavity of the main valve (71), a third oil port (B3) connected with the first oil port (P) of the power control valve (7) and a fourth oil port (B4) connected with the pilot oil return path (8), so that the reversing of the main valve (71) can be controlled.
2. The power distribution hydraulic system according to claim 1, wherein the number of the first load actuators (5) and the number of the power control valves (7) are both one, the first load actuators (5) are respectively connected with the second oil ports (a) and the third oil ports (B) of the power control valves (7), the first oil ports (P) of the power control valves (7) are connected with the fixed displacement pump (1) through the oil inlet passage (3), and the fourth oil ports (C) of the power control valves (7) are connected with the oil return passage (4) through the second load actuators (6), so that the first load actuators (5) and the second load actuators (6) can be communicated by reversing the power control valves (7).
3. The power distribution hydraulic system according to claim 1, wherein each of the first load actuators (5) is connected to the corresponding second and third oil ports (a) and (B) of the power control valve (7), respectively, the first oil port (P) of the power control valve (7) located at the front end of the load series oil path is connected to the oil-intake oil path (3), and the fourth oil port (C) of the power control valve (7) located at the rear end of the load series oil path is connected to the second load actuator (6).
4. The power distribution hydraulic system according to claim 1, characterized in that the second load actuator (6) is connected with the second port (a) and the third port (B) of one of the power control valves (7), respectively, to form a second load series unit, each of the power control valves (7) of the first load series unit is connected in series with the power control valve (7) of the second load series unit, and the fourth port (C) of the power control valve (7) of the second load series unit is connected with the oil return passage (4).
5. A power distribution hydraulic system according to claim 1, characterized in that the power control valve (7) further comprises a second non return valve (75), and the first port (P) of the power control valve (7) is in one-way communication with the main valve (71) via the second non return valve (75).
6. A power distribution hydraulic system according to claim 1, characterized in that the main valve (71) is a pilot operated directional control valve.
7. A power distribution hydraulic system according to any one of claims 1-6, characterized in that the first and second load actuators (5, 6) are connected with a pilot oil return line (8), respectively.
8. A power distribution hydraulic system according to claim 1, characterized in that the main valve (71) is integrated with the constant differential pressure valve (73).
9. A power split hydraulic system according to claim 8, wherein a first hydraulic chamber (711) and a second hydraulic chamber (712) are provided in the spool of the main valve (71), an end cover assembly (713) and a valve core (731) of the constant pressure difference valve (73) are sequentially arranged in the first hydraulic cavity (711), and a first hydraulic passage (714) communicated with the first hydraulic chamber (711) and a second hydraulic passage (715) communicated with the second hydraulic chamber (712) are provided on a spool of the main valve (71), the end cover assembly (713) is connected with a valve core (731) of the constant pressure difference valve (73) through an elastic piece (716), and a spool (731) of the constant differential pressure valve (73) is located between the first hydraulic passage (714) and the second hydraulic passage (715), so as to control the connection and disconnection of the first hydraulic pressure chamber (711) and the second hydraulic pressure chamber (712).
10. The power distribution hydraulic system according to claim 9, wherein an inner diameter of the first hydraulic chamber (711) is larger than an inner diameter of the second hydraulic chamber (712), and a stepped structure is formed at a position where the first hydraulic chamber (711) is connected to the second hydraulic chamber (712), and the spool (731) of the constant pressure differential valve (73) is connected to the elastic member (716) through a stopper (717).
11. A crane, characterized by comprising a power distribution hydraulic system according to any one of claims 1 to 10.
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| CN201911337536.1A CN111059087B (en) | 2019-12-23 | 2019-12-23 | Power distribution hydraulic system and crane |
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