CN113007157A - Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck - Google Patents
Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck Download PDFInfo
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- CN113007157A CN113007157A CN202110236728.4A CN202110236728A CN113007157A CN 113007157 A CN113007157 A CN 113007157A CN 202110236728 A CN202110236728 A CN 202110236728A CN 113007157 A CN113007157 A CN 113007157A
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- 230000007246 mechanism Effects 0.000 claims description 35
- 238000011010 flushing procedure Methods 0.000 claims description 29
- 239000003921 oil Substances 0.000 description 194
- 238000006073 displacement reaction Methods 0.000 description 8
- 230000000875 corresponding effect Effects 0.000 description 5
- 239000010720 hydraulic oil Substances 0.000 description 5
- 230000007935 neutral effect Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000002699 waste material Substances 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
- F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
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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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0423—Cooling
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to a multi-way valve and discloses a load-sensitive multi-way valve, an arm support hydraulic control system and a concrete pump truck. The load-sensitive multi-way valve not only can prevent the local oil temperature at the outlet of the variable pump and in the shell of the variable pump from being overhigh, but also has good flow stability and no overflow loss of redundant high-pressure oil.
Description
Technical Field
The invention relates to a multi-way valve, in particular to a load sensitive multi-way valve. In addition, the hydraulic control system of the arm support with the load-sensitive multi-way valve and the concrete pump truck with the hydraulic control system of the arm support are also related.
Background
The concrete pump truck is a special vehicle integrating a pumping mechanism and a boom system on a vehicle chassis. The arm support system of the concrete pump truck is mainly used for conveying and distributing concrete, namely, the arm support is controlled to be unfolded and folded through an oil cylinder, and the concrete is conveyed to a specified pouring point by matching with the rotation of a rotary table. During pouring, high requirements are placed on the stability and position accuracy of the boom mechanism, so that the small-flow stability of the boom hydraulic control valve group is required to be good, and the response time is short.
At present, the boom control valve group adopts a valve front compensation load sensitive multi-way valve controlled by electro-hydraulic proportion, after the boom reaches a specified pouring point and a concrete pump truck starts to pour, the boom only can adjust the position of the pouring point in a small range, so that after the concrete pump truck starts to pour, the boom control valve group is in a middle standby state for a long time, the reversing working time is short, and the working condition with small flow is more.
For example, the boom control valve group comprises a pressure compensation valve and a main valve core, and under a normal working condition, hydraulic oil output by the variable displacement pump flows to the main valve core through the pressure compensation valve to control the reversing of the main valve core, so that the action of an actuating mechanism is controlled; when the concrete pump truck starts to pour, the arm support control valve group is in a middle standby state for a long time, and the reversing working time is short; when the arm support control valve group is in a middle standby state, the middle position of the load sensitive multi-way valve can be in a closed state, the variable pump swings to a micro swing angle according to load feedback pressure, only micro leakage flow of the variable pump and the arm support control valve group is provided, the variable pump slowly unloads from a shell of the variable pump, and due to the fact that the unloading flow is too small, heat generated in the variable pump when the middle position is in the standby state cannot be taken away, the oil temperature of the variable pump outlet and the oil temperature of the shell are gradually increased, the service life of a variable is influenced, and the variable pump.
In contrast, a three-way flow valve is usually additionally arranged for unloading to prevent the phenomenon that the local oil temperature at the outlet of the variable pump rises; however, when the actual demand flow is smaller than the minimum flow set by the variable displacement pump, the redundant flow can overflow from the three-way flow valve, and at the moment, the stability of the flow of the working port is poor, and redundant high-pressure oil is lost, so that the waste of energy is caused.
In view of the above, there is a need to design a new load sensitive multi-way valve.
Disclosure of Invention
The invention aims to solve the technical problem of providing a load-sensitive multi-way valve which can prevent the local oil temperature at the outlet of a variable pump and in a shell of the variable pump from being too high, has good flow stability and does not have the overflow loss of redundant high-pressure oil.
The invention aims to solve the technical problem of providing an arm support hydraulic control system which can prevent the local oil temperature at the outlet of a variable pump and in a shell of the variable pump from being too high, has good flow stability and does not have the overflow loss of redundant high-pressure oil.
The invention aims to provide a concrete pump truck which has better pouring performance.
In order to solve the technical problems, the invention provides a load-sensitive multi-way valve which comprises an oil inlet pair, at least one working pair, a main oil inlet path communicated with an oil inlet of the oil inlet pair and oil inlets of the working pairs, a main oil return path communicated with an oil return port of the oil inlet pair and oil return ports of the working pairs, and a load feedback oil path communicated with a feedback oil port of the oil inlet pair and a feedback oil port of each working pair, wherein the oil inlet pair comprises a flushing mechanism which is connected between the main oil inlet path and the main oil return path so as to unload the flow pumped into the oil inlet pair when a system is in a neutral standby state.
Preferably, the oil inlet union further comprises a pressure reducing valve, the working union comprises a pressure compensation valve, a main valve and a pilot control valve group connected with a control cavity of the main valve, the pressure compensation valve is arranged on an oil path between the main oil inlet oil path and an oil inlet of the main valve, and the main oil inlet oil path is connected with the pilot control valve group through the pressure reducing valve.
Specifically, the pilot control valve group comprises two pilot valves, and each pilot valve is connected with two control cavities of the main valve in a one-to-one correspondence manner.
Furthermore, the working union also comprises a shuttle valve, an oil outlet of the shuttle valve is connected with a feedback oil port of the working union, one oil inlet of the shuttle valve is connected with a load feedback oil port of the main valve, and the other oil inlet of the shuttle valve is connected with a feedback oil port of the adjacent working union.
Preferably, the working unit further comprises a first overflow valve connected to the overflow port of the main valve so as to control the pressure of the working port of the main valve.
Particularly preferably, a throttle hole is arranged between the flushing mechanism and the main oil inlet passage.
More specifically, the flushing mechanism is a two-position, two-way solenoid valve.
Preferably, the oil inlet joint further comprises an LS unloading valve and a second overflow valve, an oil inlet of the LS unloading valve is connected with the load feedback oil path, an oil outlet of the LS unloading valve is connected with the oil tank, and the second overflow valve is connected between the main oil inlet oil path and the main oil return oil path.
The invention also discloses an arm support hydraulic control system which comprises a variable pump assembly and the load sensitive multi-way valve in any one of the technical schemes, wherein the variable pump assembly is respectively connected with the oil inlet and the feedback oil port of the oil inlet joint.
Preferably, the variable pump assembly comprises a variable control mechanism and a variable pump, the variable control mechanism comprises a constant pressure difference valve and a variable oil cylinder, an oil outlet of the variable pump is respectively connected with an oil inlet and a control cavity of the constant pressure difference valve, an oil outlet of the constant pressure difference valve is connected with a rodless cavity of the variable oil cylinder, and a feedback oil port of the oil inlet joint is connected with a spring cavity of the constant pressure difference valve so as to control the output flow of the variable pump.
The invention further discloses a concrete pump truck which comprises the boom hydraulic control system in any one of the technical schemes.
Through the technical scheme, the invention has the following beneficial effects:
the load-sensitive multi-way valve is combined with the variable pump, the flushing mechanism is arranged in the oil inlet link, when the system is in a middle standby state, the flushing mechanism is opened, and high-pressure oil pumped into the oil inlet link by the variable pump can flow back to the oil tank through the flushing mechanism, so that the problems of overhigh local oil temperature in the outlet of the conventional variable pump and the shell of the variable pump are solved, and the service life is ensured; meanwhile, when any working unit works, the flushing mechanism is closed, so that hydraulic oil flows to the working unit, the flow stability is good under the working condition of small flow, no excess high-pressure oil overflow loss exists, and energy is saved.
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 diagram of a boom hydraulic control system according to an embodiment of the present invention.
Description of the reference numerals
Oil inlet of 1 oil inlet joint and P oil inlet joint
Feedback oil port of oil return port LS oil inlet joint of T oil inlet joint
12 pressure reducing valve of 11 flushing mechanism
13-orifice 14LS unloading valve
15 second overflow valve 2 working joint
21 pressure compensating valve 22 main valve
Load feedback oil port of oil inlet LS1 main valve of P1 main valve
Oil return port of T1 main valve A1 main valve first working oil port
Second working oil port of A2 main valve and overflow oil port of B1 main valve
23 pilot valve 24 shuttle valve
25 main oil inlet path of first overflow valve 3
4 main oil return oil path 5 load feedback oil path
61 variable pump 62 constant differential pressure valve
63 variable oil cylinder
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" 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 "first", "second" 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 otherwise explicitly specified or limited, the terms "mounted," "disposed," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; 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.
It should be noted first that the load-sensitive multi-way valve of the invention belongs to the hydraulic field, for a person skilled in the art, the substantial technical idea of which lies in the hydraulic connection. The associated hydraulic components, such as directional valves, pressure reducing valves, shuttle valves, spill valves, 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 only be briefly described below. After knowing the technical idea of the present invention, those skilled in the art can also simply replace the oil path or the valve, etc. to achieve the function of the load-sensitive multi-way valve of the present invention, which also belongs to the protection scope of the present invention.
As shown in fig. 1, the load-sensitive multi-way valve according to the basic embodiment of the present invention includes an oil inlet coupler 1, at least one working coupler 2, a main oil inlet path 3 communicating an oil inlet P of the oil inlet coupler 1 with oil inlets of the working couplers 2, a main oil return path 4 communicating an oil return port T of the oil inlet coupler 1 with oil return ports of the working couplers 2, and a load feedback path 5 communicating a feedback oil port LS of the oil inlet coupler 1 with a feedback oil port of each working coupler 2, where the oil inlet coupler 1 includes a flushing mechanism 11, and the flushing mechanism 11 is connected between the main oil inlet path 3 and the main oil return path 4 to unload a flow pumped into the oil inlet coupler 1 when the system is in a neutral standby state.
According to the invention, the flushing mechanism 11 is originally added in the oil inlet union 1, after the concrete pump truck starts to pour, the arm support only can adjust the position of a pouring point in a small range, the load-sensitive multi-way valve is in a middle standby state for a long time, at the moment, the flushing mechanism 11 is controlled to be started, high-pressure oil input into the oil inlet union 1 by the variable pump flows back to an oil tank through the flushing mechanism 11, the pressure at the outlet position of the variable pump is unloaded, the heat generated when the middle position of the variable pump is in a standby state is taken away, and the oil temperature at the outlet of the variable pump and in the shell of the variable pump is; when the load sensitive multi-way valve is reversed, the flushing mechanism 11 is controlled to be closed, so that the hydraulic oil output by the variable pump can flow to the load sensitive multi-way valve completely and is used for driving the actuating mechanism to work, namely the variable pump only provides flow required by actual working conditions, no redundant high-pressure oil is lost, and energy is saved.
In order to facilitate understanding of the technical concept of the invention, the load-sensitive multi-way valve of the invention can be combined with a variable pump assembly for explanation, an oil inlet P and a feedback oil port LS of an oil inlet union 1 are respectively connected with the variable pump assembly, so that the variable pump assembly adjusts the output flow according to the load pressure information fed back to the variable pump assembly by the feedback oil port LS.
In a preferred embodiment, an orifice 13 may be installed on the oil path between the flushing mechanism 11 and the main oil inlet path 3, when the system is in a neutral standby state, the variable displacement pump assembly automatically adjusts the pumped flow rate according to the size of the orifice 13, that is, the orifice 13 limits the flushing flow rate, and the flushing mechanism 11 opens or closes the flushing flow rate, thereby effectively preventing the oil temperature at the outlet of the pump from rising.
As a specific implementation manner, the working connection 2 includes a pressure compensation valve 21, a main valve 22 and a pilot control valve group, the pilot control valve group is connected with a control cavity of the main valve 22, an oil inlet of the pressure compensation valve 21 is connected with the main oil inlet oil path 3, a working oil port of the pressure compensation valve 21 is connected with an oil inlet P1 of the main valve 22 to form a pre-valve compensation load-sensitive multi-way valve, which plays a role of balancing load, controls the front-back pressure difference of a throttling groove of the main valve 22 to be constant, ensures that the flow of the main valve 22 is only related to the valve core flow area thereof, and the other oil port of the pressure compensation valve 21 is connected with the control; the oil inlet connector 1 further comprises a pressure reducing valve 12, an oil inlet of the pressure reducing valve 12 is connected with the main oil inlet oil way 3, an oil outlet of the pressure reducing valve 12 is connected with the pilot control valve group, a pilot oil source is provided for the pilot control valve group after high-pressure oil is reduced in pressure, a pilot oil pump does not need to be additionally arranged, and cost is saved.
Specifically, the pilot control valve group may be composed of two pilot valves 23, an oil outlet of one pilot valve 23 is connected to the control cavity at one end of the main valve 22, an oil outlet of the other pilot valve 23 is connected to the control cavity at the other end of the main valve 22, and oil inlets of the two pilot valves 23 are both connected to an oil outlet of the pressure reducing valve 12; the pilot valve 23 is preferably an electromagnetic directional valve, for example, the pilot valve 23 may be a two-position three-way valve, and the pilot oil flows into the control cavity corresponding to the main valve 22 by the directional control of the two pilot valves 23 to control the directional control of the main valve 22, or the pilot valve 23 may be a two-position two-way valve, and the pilot oil flows into the control cavity corresponding to the main valve 22 by the on/off of the two pilot valves 23 to control the directional control of the main valve 22; of course, the pilot control valve group may be a three-position four-way valve, when the three-position four-way valve is in the middle position, the main valve 22 is in the middle position standby state, when the three-position four-way valve is in the left position or the right position, the control chamber at one end of the main valve 22 is communicated with the pressure reducing valve 12 through the three-position four-way valve, and the control chamber at the other end of the main valve 22 is connected with the oil tank through the three-position four-way. It should be understood that the pilot valve 23 may also be controlled by a hydraulic control or a manual control, and similarly, when the pilot valve group is a three-position four-way valve, the three-position four-way valve may also be controlled by a hydraulic control or a manual control, as long as the reversing of the main valve 22 can be controlled.
Correspondingly, the flushing mechanism 11 can be an electromagnetic valve, such as a two-position two-way valve, other equipment or a valve capable of controlling the on-off of an oil path, and when the electrical system detects that no electrical signal is input into the pilot control valve group, the flushing mechanism 11 is controlled to be powered according to a set program, so that the variable displacement pump assembly is in a low-pressure constant-pressure adjusting state, and the oil temperature at the outlet of the pump is prevented from rising. It should be noted that, in hydraulic equipment such as a concrete pump truck and the like, an electrical system generally belongs to a conventional control system, and on the basis of the conventional control system, each hydraulic element is connected with the electrical system and is controlled and operated based on an electrical signal, which is relatively mature in implementation of control technology based on the teaching of the technical idea of the present invention.
In addition, an LS unloading valve 14 and a second overflow valve 15 can be arranged in the oil inlet union 1, an oil inlet of the LS unloading valve 14 is connected with the load feedback oil path 5, an oil outlet of the LS unloading valve 14 is connected with the oil tank, when the LS unloading valve 14 is opened, the load feedback oil path 5 is communicated with the oil tank, and at the moment, a load pressure signal is not fed back to the variable pump assembly, so that the variable pump assembly does not provide hydraulic oil for the main valve 22, and misoperation is prevented; when the LS unloader valve 14 is closed, the variable displacement pump assembly normally supplies hydraulic oil to the main valve 22, so that the system normally operates; specifically, the LS unloader valve 14 may be a two-position, two-way solenoid valve that is controlled by an electrical system. And a second overflow valve 15 can be arranged on an oil path between the main oil inlet path 3 and the main oil return path 4 to limit the highest pressure of the system.
In order to screen out the maximum load pressure as a load sensitive signal to be provided to the variable displacement pump assembly, a shuttle valve 24 may be disposed in the working link 2, an oil outlet of the shuttle valve 24 is connected to a feedback oil port of the working link 2, one oil inlet of the shuttle valve 24 is connected to the load feedback oil port LS1 of the main valve 22, and the other oil inlet thereof is connected to the feedback oil port of the adjacent working link 2, so as to compare the magnitude of the load pressure of each working link 2 and feed the maximum load pressure back to the variable displacement pump assembly. It should be noted that the number of the working couplings 2 can be selected according to the needs of the actual working conditions, for example, only one working coupling 2 is provided to control the expansion and contraction of the arm support, and at this time, only one oil inlet of the shuttle valve 24 is connected with the load feedback oil port LS1 of the main valve 22, so that the load pressure can be screened out; or a plurality of working units 2 are provided, the execution of a plurality of actions is controlled, and the maximum load pressure is screened step by step through the shuttle valve 24 of each working unit 2.
In order to limit the pressure of the working port of the main valve 22 in the left or right working position, a first overflow valve 25 may be further provided, the first overflow valve 25 is connected to an overflow port B1 of the main valve 22, when the main valve 22 is in the left or right working position, the overflow port B1 is communicated with the spring cavity of the pressure compensation valve 21 through the main valve 22 in the main valve 22 to limit the highest pressure of the spring cavity of the pressure compensation valve 21, and the highest pressure of the oil outlet of the pressure compensation valve 21 is indirectly limited according to the working principle of the pressure compensation valve 21, so as to effectively limit the pressure of the working port of the main valve 22; the hydraulic ports of the main valve 22 are divided into a first hydraulic port a1 and a second hydraulic port a2, and the first hydraulic port a1 and the second hydraulic port a2 of the main valve 22 are connected to the actuator, respectively, so that the operation of the actuator can be controlled. It should be noted that a first relief valve 25 may be provided, and accordingly, a relief port B1 may be provided on the main valve 22, and the relief port B1 is designed to communicate with the spring chamber of the pressure compensation valve 21 through the main valve 22 when the main valve 22 is in the left or right operating position; alternatively, referring to fig. 1, two first relief valves 25 may be provided, and accordingly, two relief ports B1 may be provided on the main valve 22, the two first relief valves 25 are connected to the two relief ports B1 in a one-to-one correspondence, and the two relief ports B1 are designed to communicate with the spring chambers of the pressure compensating valve 21 through the main valve 22 when the main valve 22 is in the left or right operating position, respectively.
The various embodiments of the load-sensitive multi-way valve can be applied to various hydraulic control systems, such as an arm support hydraulic control system.
Specifically, the load-sensitive multi-way valve is combined with a variable pump assembly, and the variable pump assembly is respectively connected with an oil inlet P and a feedback oil port LS of an oil inlet union 1. The variable pump assembly comprises a variable control mechanism and a variable pump 61, the variable control mechanism comprises a constant pressure difference valve 62 and a variable oil cylinder 63, an oil inlet of the constant pressure difference valve 62 and a control cavity of the constant pressure difference valve are respectively connected with an oil outlet of the variable pump 61, an oil outlet of the constant pressure difference valve 62 is connected with a rodless cavity of the variable oil cylinder 63, a feedback oil port LS of an oil inlet joint 1 is connected with a spring cavity of the constant pressure difference valve 62, a load sensitive signal is provided for the constant pressure difference valve 62 through the feedback oil port LS of the oil inlet joint 1, and the constant pressure difference valve 62 adjusts a swing angle through the variable oil cylinder 63 so as to adjust the output flow of the variable pump 61.
In order to better understand the technical concept of the present invention, a relatively comprehensive technical solution of preferred technical features of the boom hydraulic control system of the present invention is described below.
The boom hydraulic control system of the preferred embodiment of the invention comprises a load-sensitive multi-way valve and a variable pump assembly, wherein the variable pump assembly comprises a variable pump 61, a constant differential pressure valve 62 and a variable oil cylinder 63; referring to fig. 1, specifically, a constant pressure valve and a constant power valve may be further selectively configured, an oil inlet and a control cavity of the constant pressure differential valve 62, an oil inlet and a control cavity of the constant pressure valve, and an oil inlet and a control cavity of the constant power valve are all connected to an oil outlet of the variable pump 61, an oil outlet of the constant pressure differential valve and an oil outlet of the constant power valve are both connected to a rodless cavity of the variable cylinder 63, an oil outlet of the constant pressure differential valve 62 is connected to a rodless cavity of the variable cylinder 63 through the constant pressure valve and the constant power valve, a spring control cavity of the constant pressure differential valve 62 is connected to a feedback oil port LS of the oil inlet manifold 1, and the constant pressure differential valve 62 adjusts a swing angle of the variable pump 61 according to a pressure difference between an outlet pressure of the variable pump 61 and a pressure of the feedback oil port LS of the oil inlet manifold 1, so. When the pressure of the oil outlet of the variable pump 61 is higher than the pressure set by the constant pressure valve, the constant pressure valve starts to work, high-pressure oil at the oil outlet enters a rodless cavity of the variable oil cylinder 63, so that the swing angle of the variable pump 61 is reduced, the higher the pressure of the oil outlet of the variable pump 61 is, the smaller the swing angle is, so as to limit the pressure of the oil outlet of the variable pump 61, for example, the variable pump 61 swings to a zero swing angle, and the pressure does not rise any more; at this time, the constant pressure valve controls the variable displacement pump 61 in preference to the constant pressure differential valve 62. When the outlet pressure of the variable pump 61 is lower than the pressure set by the constant pressure valve, the constant pressure valve is in an inoperative state, and at this time, the variable pump 61 is mainly controlled by the constant pressure differential valve 62. The constant power valve is used for limiting the maximum absorption power of the variable pump 61, that is, when the output power of the variable pump 61 is greater than the set power, the constant pressure difference valve 62 controls the variable pump 61 in preference to the constant pressure valve, so that the engine or the motor can be prevented from stopping working due to the excessive output power of the variable pump 61. That is, the combination of control of the constant pressure difference valve 62, the constant pressure valve, and the constant power valve has a priority order, the constant power valve controls the variable pump 61 in preference to the pressure difference valve, and the constant pressure valve controls the variable pump 61 in preference to the constant pressure difference valve 62. When the outlet pressure of the variable pump 61 is lower than the pressure set by the constant pressure valve, the constant pressure valve is in an inoperative state, and the constant pressure difference valve 62 controls the variable pump 61, a part of the flow output by the variable pump 61 flows in through the oil inlet P of the oil inlet union 1, when the system normally works, after the high-pressure oil is decompressed by the decompression valve 12, the pilot oil is provided for the pilot valve 23, the electric system controls the corresponding pilot valve 23 to be electrified, so that the main valve 22 is reversed, another part of the flow output by the variable pump 61 flows to the main valve 22 through the pressure compensation valve 21, and then flows to the execution mechanism through the first working oil port a1 or the second working oil port a2 of the main valve 22, so that the corresponding action control is realized; when the concrete pump truck starts to pour, the system is in a middle standby state, the electrical system detects that no electric signal is input to all the pilot valves 23, and after a certain time (set in a program), the flushing mechanism 11 is controlled to be started, so that the variable pump 61 is in a low-pressure constant-pressure adjusting state, and according to the size of the throttling hole 13, the variable pump 61 pumps out corresponding flushing flow to avoid the rise of the oil temperature in the outlet of the variable pump 61 and the shell; when the electrical system detects that any pilot valve 23 has an input electrical signal, the flushing mechanism 11 is controlled to close, the flushing flow is closed, the working unit 2 starts to work, the shuttle valve 24 screens out the maximum load pressure as a load sensitive signal to be provided to the constant differential pressure valve 62, the constant differential pressure valve 62 automatically adjusts the swing angle of the variable pump 61 according to the fed back LS (load sensitive) pressure signal, only the flow required by the actual working condition of the working unit 2 is provided, the stability of the small flow is good, and no redundant flow loss exists. By arranging the flushing mechanism 11, the boom hydraulic control system of the concrete pump truck has good small-flow stability and quick response time during pouring; the requirements on the position precision of a pouring point and the stability of the arm support structure are effectively met.
The embodiment of the concrete pump truck of the invention can be provided with the boom hydraulic control system described in the embodiment, namely, all technical schemes of the boom hydraulic control system embodiment are adopted, so that the concrete pump truck at least has all beneficial effects brought by the technical schemes of the boom hydraulic control system embodiment. Of course, the boom hydraulic control system of the invention can also be applied to other hydraulic equipment which needs to control the oil temperature in the system in a neutral standby state.
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. The load-sensitive multi-way valve is characterized by comprising an oil inlet connector (1), at least one working connector (2), a main oil inlet oil way (3) for communicating an oil inlet (P) of the oil inlet connector (1) with oil inlets of the working connectors (2), a main oil return oil way (4) for communicating oil return ports (T) of the oil inlet connector (1) with oil return ports of the working connectors (2) and a load feedback oil way (5) for communicating feedback oil ports (LS) of the oil inlet connector (1) with feedback oil ports of the working connectors (2), wherein the oil inlet connector (1) comprises a flushing mechanism (11), and the flushing mechanism (11) is connected between the main oil inlet oil way (3) and the main oil return oil way (4) so as to pump the flow unloading of the oil inlet connector (1) when the system is in a middle standby state.
2. The load-sensitive multi-way valve according to claim 1, wherein the oil inlet union (1) further comprises a pressure reducing valve (12), the working union (2) comprises a pressure compensation valve (21), a main valve (22) and a pilot control valve group connected with a control cavity of the main valve (22), the pressure compensation valve (21) is arranged on an oil path between the main oil inlet path (3) and an oil inlet (P1) of the main valve (22), and the main oil inlet path (3) is connected with the pilot control valve group through the pressure reducing valve (12).
3. The load-sensitive multiple-way valve according to claim 2, characterized in that the pilot valve group comprises two pilot valves (23), each pilot valve (23) being connected to two control chambers of the main valve (22) in a one-to-one correspondence.
4. The load-sensitive multi-way valve according to claim 2, characterized in that the working link (2) further comprises a shuttle valve (24), an oil outlet of the shuttle valve (24) is connected with a feedback oil port of the working link (2), and an oil inlet of the shuttle valve (24) is connected with a load feedback oil port (LS1) of the main valve (22), and another oil inlet thereof is connected with a feedback oil port of the adjacent working link (2).
5. The load-sensitive multi-way valve according to claim 2, characterized in that the working train further comprises a first relief valve (25), the first relief valve (25) being connected with a relief port (B1) of the main valve (22) to enable control of the pressure of the working port of the main valve (22).
6. Load sensitive multiple-way valve according to any one of claims 1 to 5, characterized in that an orifice (13) is provided between the flushing means (11) and the main oil inlet circuit (3).
7. Load sensitive multiple-way valve according to one of claims 1 to 5, characterized in that the flushing mechanism (11) is a two-position, two-way solenoid valve.
8. The load-sensitive multi-way valve according to any one of claims 1 to 5, wherein the oil inlet joint (1) further comprises an LS unloading valve (14) and a second overflow valve (15), an oil inlet of the LS unloading valve (14) is connected with the load feedback oil way (5), an oil outlet of the LS unloading valve is connected with an oil tank, and the second overflow valve (15) is connected between the main oil inlet oil way (3) and the main oil return oil way (4).
9. An arm support hydraulic control system is characterized by comprising a variable pump assembly and a load sensitive multi-way valve according to any one of claims 1 to 8, wherein the variable pump assembly is respectively connected with an oil inlet (P) and a feedback oil port (LS) of an oil inlet joint (1).
10. The boom hydraulic control system of claim 9, wherein the variable pump assembly comprises a variable control mechanism and a variable pump (61), the variable control mechanism comprises a constant pressure difference valve (62) and a variable oil cylinder (63), an oil outlet of the variable pump (61) is connected with an oil inlet of the constant pressure difference valve (62) and a control cavity respectively, an oil outlet of the constant pressure difference valve (62) is connected with a rodless cavity of the variable oil cylinder (63), and a feedback oil port (LS) of the oil inlet joint (1) is connected with a spring cavity of the constant pressure difference valve (62) so as to control the output flow of the variable pump (61).
11. Concrete pump truck characterized in that it comprises a boom hydraulic control system according to claim 9 or 10.
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| CN202110236728.4A CN113007157A (en) | 2021-03-03 | 2021-03-03 | Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck |
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| CN202110236728.4A CN113007157A (en) | 2021-03-03 | 2021-03-03 | Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck |
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Effective date of registration: 20220718 Address after: 415001 No. 321, Deshan Avenue, Deshan economic development zone, Changde City, Hunan Province Applicant after: CHANGDE ZHONGLIAN ZHONGKE HYDRAULIC Co.,Ltd. Address before: 410013 No. 361 South silver basin, Changsha, Hunan, Yuelu District Applicant before: ZOOMLION HEAVY INDUSTRY SCIENCE&TECHNOLOGY Co.,Ltd. |
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