CN112343881B - Balanced pressure self preservation protects hydraulic system - Google Patents
Balanced pressure self preservation protects hydraulic system Download PDFInfo
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- CN112343881B CN112343881B CN202011272537.5A CN202011272537A CN112343881B CN 112343881 B CN112343881 B CN 112343881B CN 202011272537 A CN202011272537 A CN 202011272537A CN 112343881 B CN112343881 B CN 112343881B
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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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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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
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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
- F15B13/027—Check valves
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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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
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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
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- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a balanced pressure self-protection hydraulic system, which comprises an oil tank, a self-balanced protection hydraulic system and a pressure balance system, wherein the oil tank is connected with the self-balanced protection hydraulic system; the pressure balance system comprises a first variable amplitude oil cylinder, a first balance valve, a second variable amplitude oil cylinder, a third balance valve, a fourth balance valve, a control oil port LA and a control oil port LB; the self-balancing protection hydraulic system comprises a first bidirectional motor, a fifth balance valve, a sixth balance valve, a second bidirectional motor, a first explosion-proof valve, a second explosion-proof valve, a control oil port WA, a control oil port WB and an oil return port WT; by utilizing the hydraulic system, the pressure of the two variable amplitude oil cylinders is automatically balanced, and the phenomenon that the two variable amplitude oil cylinders are blocked is effectively avoided; meanwhile, the stability and the safety of the bidirectional hydraulic motor can be improved by utilizing the first explosion-proof valve and the second explosion-proof valve.
Description
Technical Field
The invention relates to a hydraulic system, in particular to a balanced pressure self-protection hydraulic system.
Background
The double oil cylinders of the actuating mechanism in the prior art solve the problem of different pressures of the two oil cylinders by installing a balance valve.
The application document with the application number of 201110365008.4 and the publication date of 2012.6.20 discloses a double-oil-cylinder synchronous system of a bridge detection operation vehicle, the system at least comprises a double-drive oil cylinder, a balance valve and two one-way back pressure valves for independently adjusting back pressure, the double-drive oil cylinder is a double-action oil cylinder, two ends of each drive oil cylinder are respectively hinged with a fixing seat and a U-shaped cross-section working platform, the two drive oil cylinders and oil ways thereof are connected in parallel, the one-way back pressure valves are respectively connected between working oil ports of rod cavities of the two drive oil cylinders and the balance valve, or are not connected between the rod cavity oil ports of the two drive oil cylinders and the direction valve through the balance valve, and the rodless cavity oil ways of the two drive oil cylinders are respectively connected with another working oil port of the balance valve after being converged. The substitute of the one-way back pressure valve is a one-way back pressure valve group for independently adjusting back pressure.
But oil ports of rod cavities of two driving oil cylinders of the system are only connected with one-way back pressure valve; meanwhile, the two one-way back pressure valves are respectively connected with the balance valve, and the two one-way back pressure valves are not connected; when hydraulic oil flows in from the port A of the balance valve, the hydraulic oil flows through one of the driving oil cylinders and the one-way back pressure valve connected with the driving oil cylinder, and then flows out from the port B of the balance valve; hydraulic oil cannot circulate between the two driving oil cylinders; the pressure balance of the two driving oil cylinders can not be realized, so that when two one-way back pressure valve sections are inconsistent or the performances are different, the pressure between the two driving oil cylinders is different, and the driving oil cylinders can shake during working. Meanwhile, when the pipeline in the system leaks or explodes, the communication oil port cannot be automatically closed, so that the safety and the reliability of the system are low.
Disclosure of Invention
The invention provides a balanced pressure self-protection hydraulic system, which is used for realizing automatic balance of the pressure of two amplitude-variable oil cylinders and effectively avoiding the phenomenon that the two amplitude-variable oil cylinders are blocked; meanwhile, the stability and the safety of the bidirectional hydraulic motor can be improved by utilizing the first explosion-proof valve and the second explosion-proof valve.
In order to achieve the purpose, the technical scheme of the invention is as follows: a balanced pressure self-protection hydraulic system comprises an oil tank, a self-balanced protection hydraulic system and a pressure balance system; the self-balancing protection hydraulic system and the pressure balance system are connected with the oil tank; the pressure balance system comprises a first variable amplitude oil cylinder, a first balance valve, a second variable amplitude oil cylinder, a third balance valve, a fourth balance valve, a control oil port LA and a control oil port LB; the self-balancing protection hydraulic system comprises a first bidirectional motor, a fifth balance valve, a sixth balance valve, a second bidirectional motor, a first explosion-proof valve, a second explosion-proof valve, a control oil port WA, a control oil port WB and an oil return port WT; the control oil port LA and the control oil port WA are connected with one oil port of the oil tank, the control oil port WB and the control oil port LB are connected with the other oil port of the oil tank, and the oil return port WT is connected with an oil return port of the oil tank;
the first variable-amplitude oil cylinder, the second variable-amplitude oil cylinder and the oil circuit connection thereof are connected in parallel, rodless cavities of the first variable-amplitude oil cylinder and the second variable-amplitude oil cylinder are both connected with a control oil port LB, and rod cavities of the first variable-amplitude oil cylinder and the second variable-amplitude oil cylinder are both connected with a control oil port LA;
the first balance valve is connected between the rodless cavity opening of the first luffing oil cylinder and the control oil port LB; the fourth balance valve is connected between the rodless cavity opening of the second variable amplitude oil cylinder and the control oil port LB; the rodless cavity port of the first luffing oil cylinder is also connected with a second balance valve; the rodless cavity opening of the second variable amplitude oil cylinder is also connected with a third balance valve; the second balance valve is also connected with the third balance valve; control oil ports of the first balance valve, the second balance valve, the third balance valve and the fourth balance valve are all connected with a control oil port LA;
the first and second bidirectional motors and the oil ways thereof are connected in parallel, one ends of the first and second bidirectional motors are connected with a control oil port WA, and the other ends of the first and second bidirectional motors are connected with an oil return port WB; oil drain ports of the first bidirectional motor and the second bidirectional motor are connected with an oil return port WT; the control oil port WA, the control oil port WB and the oil return port WB are connected with an oil tank;
the fifth balance valve is connected between the other end of the first bidirectional motor and the control oil port WB; the sixth balance valve is connected between the other end of the second bidirectional motor and the control oil port WB; the other end of the first bidirectional motor is also connected with a first explosion-proof valve; the other end of the second bidirectional motor is also connected with a second explosion-proof motor; the first explosion-proof valve is also connected with the second explosion-proof valve; and control oil ports of the fifth balance valve and the sixth balance valve are also connected with a control oil port WA.
Further, the first balance valve comprises a first check valve and a first overflow valve; an oil inlet of the first overflow valve is connected with a rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the first overflow valve is connected with a control oil port LB; a control oil port of the first overflow valve is connected with a control oil port LA; an oil inlet of the first check valve is connected with an oil outlet of the first overflow valve, and an oil outlet of the first check valve is connected with an oil inlet of the first overflow valve.
Further, the fourth balancing valve comprises a fourth one-way valve and a fourth overflow valve; an oil inlet of the fourth overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, an oil outlet of the fourth overflow valve is connected with a control oil port LB, and a control oil port of the fourth overflow valve is connected with a control oil port LA; an oil inlet of the fourth one-way valve is connected with an oil outlet of the fourth overflow valve, and an oil outlet of the fourth one-way valve is connected with a rodless cavity opening of the second variable amplitude oil cylinder.
Further, the second balance valve comprises a second check valve and a second overflow valve; the third balance valve comprises a third check valve and a third overflow valve; an oil inlet of the second overflow valve is connected with the rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the second overflow valve is connected with an oil outlet of the third overflow valve; a control oil port of the second overflow valve is connected with a control oil port of the first overflow valve; an oil inlet of a third overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, and a control oil port of the third overflow valve is connected with a control oil port of a fourth overflow valve; an oil inlet of the second one-way valve is connected with an oil outlet of the second overflow valve, and an oil outlet of the second one-way valve is connected with an oil inlet of the second overflow valve; an oil inlet of the third one-way valve is connected with an oil outlet of the third overflow valve, and an oil outlet of the third one-way valve is connected with an oil inlet of the second overflow valve.
Further, the fifth balance valve comprises a fifth check valve and a fifth overflow valve; an oil inlet of a fifth overflow valve is connected with the other end of the first bidirectional motor, and an oil outlet of the fifth overflow valve is connected with a control oil port WB; a control oil port of the fifth overflow valve is connected with a control oil port WA; an oil inlet of the fifth one-way valve is connected with an oil outlet of the fifth overflow valve, and an oil outlet of the fifth one-way valve is connected with an oil inlet of the fifth overflow valve.
Further, the sixth balancing valve comprises a sixth check valve and a sixth overflow valve; an oil inlet of the sixth overflow valve is connected with the other end of the second bidirectional motor, and an oil outlet of the sixth overflow valve is connected with a control oil port WB; a control oil port of the sixth overflow valve is connected with the control oil port WA; an oil outlet of the sixth one-way valve is connected with an oil inlet of the sixth overflow valve.
Furthermore, a port B of the first explosion-proof valve is connected with the other end of the first bidirectional motor, a port F of the first explosion-proof valve is connected with a port F of the second explosion-proof valve, a port B of the second explosion-proof valve is connected with the other end of the second bidirectional motor, a first throttle valve in the first explosion-proof valve is arranged close to the port F of the first explosion-proof valve, and a second throttle valve in the second explosion-proof valve is arranged close to the port F of the second explosion-proof valve.
Furthermore, the control oil ports LA, LB, WA and WB are connected with an oil tank through a hydraulic pump by a reversing valve.
The working principle of the pressure balance system is as follows: the hydraulic oil is pumped into the control oil port LA through the reversing valve by the hydraulic pump, the hydraulic oil respectively enters the first amplitude cylinder and the second amplitude cylinder from the control oil port LA, meanwhile, the hydraulic oil of the control oil port LA is respectively input into the control oil port of the first balance valve, the second balance valve, the third balance valve and the fourth balance valve, in the process of feeding the hydraulic oil, the hydraulic oil in the rodless cavity of the first amplitude cylinder flows back to the control oil port LB through the first balance valve and then flows back to the oil tank, and meanwhile, the hydraulic oil in the rodless cavity of the second amplitude cylinder flows back to the control oil port LB through the third balance valve and then flows back to the oil tank. In the process, if the oil pressure in the rodless cavities of the first luffing oil cylinder and the second luffing oil cylinder is unbalanced, the oil pressure in the rodless cavities is balanced through the second balance valve and the third balance valve, specifically, if the oil pressure in the rodless cavity of the first luffing oil cylinder is greater than the oil pressure in the rodless cavity of the second luffing oil cylinder, under the action of the second balance valve and the third balance valve, part of hydraulic oil in the rodless cavity of the first luffing oil cylinder flows into the rodless cavity of the second luffing oil cylinder through the second balance valve and the third balance valve, otherwise, the hydraulic oil flows reversely.
If the hydraulic oil flows in from the control oil port LB through the control reversing valve, the hydraulic oil enters the first amplitude-variable oil cylinder through the first balance valve, and the return oil of the first amplitude-variable oil cylinder flows back from the control oil port LA; meanwhile, hydraulic oil enters the second variable amplitude oil cylinder through the fourth balance valve, and return oil of the second variable amplitude oil cylinder flows back from the control oil port LA; in the process, if the oil pressure in the rodless cavities of the first luffing oil cylinder and the second luffing oil cylinder is unbalanced, the oil pressure in the rodless cavities is balanced through the second balance valve and the third balance valve, specifically, if the oil pressure in the rodless cavity of the first luffing oil cylinder is greater than the oil pressure in the rodless cavity of the second luffing oil cylinder, under the action of the second balance valve and the third balance valve, part of hydraulic oil in the rodless cavity of the first luffing oil cylinder flows into the rodless cavity of the second luffing oil cylinder through the second balance valve and the third balance valve, otherwise, the hydraulic oil flows reversely.
The working principle of the self-balancing protection hydraulic system is as follows: the hydraulic oil is pumped into the control oil port WA through the reversing valve by the hydraulic pump, the hydraulic oil respectively enters the first bidirectional motor and the second bidirectional motor from the control oil port WA, meanwhile, the hydraulic oil of the control oil port WA is respectively input into the control oil port of the fifth balance valve and the control oil port of the sixth balance valve, in the process of feeding the hydraulic oil, the hydraulic oil flows back to the control oil port WB from the first bidirectional motor through the fifth balance valve and then flows back to the oil tank, and meanwhile, the hydraulic oil flows back to the control oil port WB from the second bidirectional motor through the sixth balance valve and then flows back to the oil tank. In the process, when the oil pressure between the first bidirectional motor and the second bidirectional motor is unbalanced, because the first explosion-proof valve and the second explosion-proof valve are communicated in two directions during normal operation, the first bidirectional motor and the second bidirectional motor are communicated through the first explosion-proof valve and the second explosion-proof valve, the oil pressure of the first bidirectional motor and the oil pressure of the second bidirectional motor are automatically balanced, if the oil quantity of the output end of one bidirectional motor is obviously reduced due to failure and the like, the oil pressure of the output end of the other bidirectional motor is larger than that of the other bidirectional motor, and thus the explosion-proof valve close to the end with the large oil pressure is cut off to avoid the phenomenon of oil leakage of the two bidirectional motors, so that the other bidirectional motor can normally operate, and the one bidirectional motor can be better protected.
In the pressure balance system, due to the arrangement of the first balance valve, the first balance valve can prevent the first luffing cylinder from undesirably moving downwards and allow an operator to enable the first luffing cylinder to move upwards at a certain speed and keep at a certain position; in addition, the first balance valve can be used for placing actions generated by actions prior to the hydraulic pump due to load energy on the first luffing oil cylinder, so that the cavitation phenomenon and the load runaway phenomenon of the first luffing oil cylinder are effectively eliminated; furthermore, the first balancing valve can prevent the runaway of the moving load when the pipe in the hydraulic circuit bursts or seriously leaks.
Similarly, for the fourth balancing valve and the second luffing cylinder, the function of the fourth balancing valve relative to the second luffing cylinder is the same as the function of the first balancing valve relative to the first luffing cylinder.
In addition, due to the fact that the second balance valve and the third balance valve are arranged, the pressure of the first amplitude-changing oil cylinder and the pressure of the second amplitude-changing oil cylinder can be balanced, the first amplitude-changing oil cylinder and the second amplitude-changing oil cylinder are better in synchronism, and the phenomenon that the first amplitude-changing oil cylinder and the second amplitude-changing oil cylinder are clamped is avoided.
If the hydraulic oil flows in from the control oil port WB through the control reversing valve, the hydraulic oil enters the first bidirectional motor through the fifth balance valve, and return oil of the first bidirectional motor flows back from the control oil port WA; meanwhile, the hydraulic oil enters the second bidirectional motor through the sixth balance valve, and the return oil of the second bidirectional motor flows back from the control oil port WA.
Therefore, the system can not only balance the pressure and the oil pressure of the two bidirectional motors and effectively reduce the vibration, but also ensure the normal work of one bidirectional motor when the oil pressure is overlarge and protect the other bidirectional motor so as to improve the safety and the stability of the hydraulic system.
Drawings
FIG. 1 is a block diagram of a balanced pressure self-protection hydraulic system.
Fig. 2 is a schematic diagram of a pressure equalization system of the present invention.
Fig. 3 is a schematic diagram of a self-balancing protection hydraulic system according to the present invention.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1-3; a balanced pressure self-protection hydraulic system comprises an oil tank, a self-balanced protection hydraulic system and a pressure balance system; the self-balancing protection hydraulic system and the pressure balance system are connected with the oil tank; the pressure balance system comprises a first luffing oil cylinder 51, a first balance valve 1, a second balance valve 2, a second luffing oil cylinder 52, a third balance valve 3, a fourth balance valve 4, a control oil port LA and a control oil port LB; the self-balancing protection hydraulic system comprises a first bidirectional motor 53, a fifth balance valve 6, a sixth balance valve 7, a second bidirectional motor 54, a first explosion-proof valve 8, a second explosion-proof valve 9, a control oil port WA, a control oil port WB and an oil return port WT; the control oil port LA and the control oil port WA are connected with one oil port of the oil tank, the control oil port WB and the control oil port LB are connected with the other oil port of the oil tank, and the oil return port WT is connected with an oil return port of the oil tank.
The first luffing oil cylinder 51, the second luffing oil cylinder 52 and the oil circuit connection thereof are connected in parallel, rodless cavities of the first luffing oil cylinder 51 and the second luffing oil cylinder 52 are both connected with a control oil port LB, and rodless cavities of the first luffing oil cylinder 51 and the second luffing oil cylinder 52 are both connected with a control oil port LA.
The first balance valve 1 is connected between the rodless cavity opening of the first variable amplitude oil cylinder 51 and the control oil port LB; the fourth balance valve 4 is connected between the rodless cavity opening of the second luffing cylinder 52 and the control oil opening LB; the rodless cavity opening of the first luffing cylinder 51 is also connected with the second balance valve 2; the rodless cavity opening of the second luffing cylinder 52 is also connected with the third balanced valve 3; the second balance valve 2 is also connected with a third balance valve 3; the control ends of the first balance valve 1, the second balance valve 2, the third balance valve 3 and the fourth balance valve 4 are all connected with a control oil port LA.
The first balance valve 1 comprises a first check valve 12 and a first overflow valve 11 which are connected in parallel; the second balance valve 2 comprises a second check valve 22 and a second overflow valve 21 which are connected in parallel; the third balance valve 3 comprises a third check valve 32 and a third overflow valve 31 which are connected in parallel; the fourth balancing valve 4 comprises a fourth non return valve 42 and a fourth overflow valve 41 connected in parallel.
An oil inlet of the first overflow valve 11 is connected with a rodless cavity opening of the first variable amplitude oil cylinder 51, and an oil outlet of the first overflow valve 11 is connected with a control oil port LB; the control port of the first overflow valve 11 is connected to the control port LA.
An oil inlet of the first check valve 12 is connected with an oil outlet of the first overflow valve 11, and an oil outlet of the first check valve 12 is connected with an oil inlet of the first overflow valve 11.
An oil inlet of the second overflow valve 21 is connected with a rodless cavity port of the first luffing oil cylinder 51, and an oil outlet of the second overflow valve 21 is connected with an oil outlet of the third overflow valve 31; a control oil port of the second overflow valve 21 is connected with a control oil port of the first overflow valve 11; an oil inlet of the third overflow valve 31 is connected with a rodless cavity port of the second luffing oil cylinder 52, and a control oil port of the third overflow valve 31 is connected with a control oil port of the fourth overflow valve 41.
An oil inlet of the second check valve 22 is connected with an oil outlet of the second overflow valve 21, and an oil outlet of the second check valve 22 is connected with an oil inlet of the second overflow valve 21; an oil inlet of the third check valve 32 is connected with an oil outlet of the third overflow valve 31, and an oil outlet of the third check valve 32 is connected with an oil inlet of the second overflow valve 21.
An oil inlet of the fourth overflow valve 41 is connected with a rodless cavity opening of the second luffing cylinder 52, an oil outlet of the fourth overflow valve 41 is connected with a control oil port LB, and a control oil port of the fourth overflow valve 41 is connected with a control oil port LA.
An oil inlet of the fourth one-way valve 42 is connected with an oil outlet of the fourth overflow valve 41, and an oil outlet of the fourth one-way valve 42 is connected with a rodless cavity opening of the second luffing cylinder 52.
The working principle of the pressure balance system is as follows: hydraulic oil is pumped into the control oil port LA through the reversing valve by the hydraulic pump, the hydraulic oil respectively enters the first amplitude cylinder 51 and the second amplitude cylinder 52 from the control oil port LA, meanwhile, the hydraulic oil of the control oil port LA is respectively input into the control oil ports of the first balance valve 1, the second balance valve 2, the third balance valve 3 and the fourth balance valve 4, in the process of feeding the hydraulic oil, the hydraulic oil in the rodless cavity of the first amplitude cylinder 51 flows back to the control oil port LB through the first balance valve 1 and then flows back to the oil tank, and meanwhile, the hydraulic oil in the rodless cavity of the second amplitude cylinder 52 flows back to the control oil port LB through the third balance valve 3 and then flows back to the oil tank. In the above process, when the oil pressures in the rodless cavities of the first luffing cylinder 51 and the second luffing cylinder are unbalanced, the oil pressures in the rodless cavities are balanced by the second balance valve 2 and the third balance valve 3, specifically, if the oil pressure in the rodless cavity of the first luffing cylinder 51 is greater than the oil pressure in the rodless cavity of the second luffing cylinder 52, under the action of the second balance valve 2 and the third balance valve 3, part of the hydraulic oil in the rodless cavity of the first luffing cylinder 51 flows into the rodless cavity of the second luffing cylinder 52 through the second balance valve 2 and the third balance valve 3, otherwise, the hydraulic oil flows in the reverse direction.
If the hydraulic oil flows in from the control oil port LB through the control reversing valve, the hydraulic oil enters the first luffing cylinder 51 through the first balance valve 1, and the return oil of the first luffing cylinder 51 flows back from the control oil port LA; meanwhile, the hydraulic oil enters the second luffing cylinder 52 through the fourth balance valve 4, and the return oil of the second luffing cylinder 52 flows back from the control oil port LA; in the above process, when the oil pressures in the rodless cavities of the first luffing cylinder 51 and the second luffing cylinder are unbalanced, the oil pressures in the rodless cavities are balanced by the second balance valve 2 and the third balance valve 3, specifically, if the oil pressure in the rodless cavity of the first luffing cylinder 51 is greater than the oil pressure in the rodless cavity of the second luffing cylinder 52, under the action of the second balance valve 2 and the third balance valve 3, part of the hydraulic oil in the rodless cavity of the first luffing cylinder 51 flows into the rodless cavity of the second luffing cylinder 52 through the second balance valve 2 and the third balance valve 3, otherwise, the hydraulic oil flows in the reverse direction.
In the pressure balance system, due to the arrangement of the first balance valve 1, in the direction of a visual angle shown in fig. 2, the first balance valve 1 can prevent the first luffing cylinder 51 from undesirably moving downwards and allow an operator to move the first luffing cylinder 51 upwards at a certain speed and keep the first luffing cylinder 51 at a certain position; in addition, the first balance valve 1 can be used for placing actions generated by actions prior to the hydraulic pump due to load energy on the first luffing cylinder 51, so that the cavitation phenomenon and the load runaway phenomenon of the first luffing cylinder 51 are effectively eliminated; furthermore, the first counter balance valve 1 prevents the runaway of the moving load when the line in the hydraulic circuit bursts or leaks seriously.
Likewise, the action of the fourth balancing valve 4 with respect to the second luffing cylinder 52 is the same for the fourth balancing valve 4 and the second luffing cylinder 52 as for the first balancing valve 1 with respect to the first luffing cylinder 51.
In addition, due to the arrangement of the second and third balance valves, the pressure of the first luffing cylinder 51 and the second luffing cylinder 52 can be balanced, the synchronism of the first luffing cylinder 51 and the second luffing cylinder 52 is better, and the phenomenon that the first luffing cylinder 51 and the second luffing cylinder 52 are blocked is avoided.
The first and second bidirectional motors 53 and 54 and the oil passages thereof are connected in parallel, one ends of the first and second bidirectional motors 53 and 54 are connected to the control port WA, and the other ends of the first and second bidirectional motors 53 and 54 are connected to the return port WB; the drain ports of the first and second bidirectional motors 53 and 54 are connected to the oil return port WT; the control oil port WA, the control oil port WB and the oil return port WB are connected with an oil tank.
The fifth balance valve 6 is connected between the other end of the first bidirectional motor 53 and the control oil port WB; the sixth balance valve 7 is connected between the other end of the second bidirectional motor 54 and the control port WB; the other end of the first bidirectional motor 53 is also connected with the first explosion-proof valve 8; the other end of the second bidirectional motor 54 is also connected with a second explosion-proof valve 9; the first explosion-proof valve 8 is also connected with a second explosion-proof valve 9; the control oil ports of the fifth balance valve 6 and the sixth balance valve 7 are also connected with a control oil port WA.
The fifth balancing valve 6 includes a fifth check valve 62 and a fifth relief valve 61; the sixth balancing valve 7 includes a sixth check valve 72 and a sixth relief valve 71.
An oil inlet of the fifth overflow valve 61 is connected with the other end of the first bidirectional motor 53, and an oil outlet of the fifth overflow valve 61 is connected with a control oil port WB; the control port of the fifth relief valve 61 is connected to the control port WA.
An oil inlet of the sixth overflow valve 71 is connected with the other end of the second bidirectional motor 54, and an oil outlet of the sixth overflow valve 71 is connected with a control oil port WB; a control port of the fifth spill valve 61 is connected to the control port WA.
The port B of the first explosion-proof valve 8 is connected with the other end of the first bidirectional motor 53, the port F of the first explosion-proof valve 8 is connected with the port F of the second explosion-proof valve 9, the port B of the second explosion-proof valve 9 is connected with the other end of the second bidirectional motor 54, the first throttle valve 83 in the first explosion-proof valve 8 is arranged close to the port F of the first explosion-proof valve 8, and the second throttle valve 93 in the second explosion-proof valve 9 is arranged close to the port F of the second explosion-proof valve 9.
The working principle of the self-balancing protection hydraulic system is as follows: hydraulic oil is pumped by a hydraulic pump through a reversing valve to enter a control oil port WA, the hydraulic oil respectively enters the first bidirectional motor 53 and the second bidirectional motor 54 from the control oil port WA, meanwhile, the hydraulic oil of the control oil port WA is respectively input into the control oil ports of the fifth balance valve 6 and the sixth balance valve 7, in the process of feeding the hydraulic oil, the hydraulic oil flows back to the control oil port WB from the first bidirectional motor 53 through the fifth balance valve 6 and then flows back to the oil tank, and meanwhile, the hydraulic oil flows back to the control oil port WB from the second bidirectional motor 54 through the sixth balance valve 7 and then flows back to the oil tank. In the above process, when the oil pressure between the first bidirectional motor 53 and the second bidirectional motor 54 is unbalanced, because the first explosion-proof valve 8 and the second explosion-proof valve 9 are communicated in two directions during normal operation, in this way, the first and second bidirectional motors are communicated through the first explosion-proof valve 8 and the second explosion-proof valve 9, so that the oil pressure of the first and second bidirectional motors is automatically balanced, if the oil volume at the output end of one of the bidirectional motors is significantly reduced due to a fault or the like, the oil pressure at the output end of the other bidirectional motor is greater than that of one of the bidirectional motors, in this way, the explosion-proof valve near the end with the large oil pressure is turned off, and the phenomenon of oil cross between the two bidirectional motors is avoided, so that the other bidirectional motor can operate normally, and one of the bidirectional motors can be better protected.
If the hydraulic oil flows in from the control oil port WB through the control reversing valve, the hydraulic oil enters the first bidirectional motor 53 through the fifth balance valve 6, and the return oil of the first bidirectional motor 53 flows back from the control oil port WA; meanwhile, the hydraulic oil enters the second bidirectional motor 54 through the sixth balance valve 7, and the return oil of the second bidirectional motor 54 flows back from the control port WA.
Therefore, the system can not only balance the pressure and the oil pressure of the two bidirectional motors and effectively reduce the vibration, but also ensure the normal work of one bidirectional motor when the oil pressure is overlarge and protect the other bidirectional motor so as to improve the safety and the stability of the hydraulic system.
Claims (8)
1. The utility model provides a balanced pressure self preservation protects hydraulic system which characterized in that: the system comprises an oil tank, a self-balancing protection hydraulic system and a pressure balancing system; the self-balancing protection hydraulic system and the pressure balance system are connected with the oil tank; the pressure balance system comprises a first variable amplitude oil cylinder, a first balance valve, a second variable amplitude oil cylinder, a third balance valve, a fourth balance valve, a control oil port LA and a control oil port LB; the self-balancing protection hydraulic system comprises a first bidirectional motor, a fifth balance valve, a sixth balance valve, a second bidirectional motor, a first explosion-proof valve, a second explosion-proof valve, a control oil port WA, a control oil port WB and an oil return port WT; the control oil port LA and the control oil port WA are connected with one oil port of the oil tank, the control oil port WB and the control oil port LB are connected with the other oil port of the oil tank, and the oil return port WT is connected with an oil return port of the oil tank;
the first amplitude-variable oil cylinder, the second amplitude-variable oil cylinder and the oil circuit connection thereof are connected in parallel, rodless cavities of the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder are both connected with a control oil port LB, and rod cavities of the first amplitude-variable oil cylinder and the second amplitude-variable oil cylinder are both connected with a control oil port LA;
the first balance valve is connected between the rodless cavity opening of the first variable amplitude oil cylinder and the control oil port LB; the fourth balance valve is connected between the rodless cavity opening of the second variable amplitude oil cylinder and the control oil port LB; the rodless cavity port of the first luffing oil cylinder is also connected with a second balance valve; the rodless cavity port of the second variable amplitude oil cylinder is also connected with a third balance valve; the second balance valve is also connected with a third balance valve; control oil ports of the first balance valve, the second balance valve, the third balance valve and the fourth balance valve are all connected with a control oil port LA;
the first and second bidirectional motors and the oil ways thereof are connected in parallel, one ends of the first and second bidirectional motors are connected with a control oil port WA, and the other ends of the first and second bidirectional motors are connected with an oil return port WB; the oil drainage ports of the first bidirectional motor and the second bidirectional motor are connected with an oil return port WT; the control oil port WA, the control oil port WB and the oil return port WB are connected with an oil tank;
the fifth balance valve is connected between the other end of the first bidirectional motor and the control oil port WB; the sixth balance valve is connected between the other end of the second bidirectional motor and the control oil port WB; the other end of the first bidirectional motor is also connected with a first explosion-proof valve; the other end of the second bidirectional motor is also connected with a second explosion-proof valve; the first explosion-proof valve is also connected with the second explosion-proof valve; and control oil ports of the fifth balance valve and the sixth balance valve are also connected with a control oil port WA.
2. The balanced pressure self-protection hydraulic system of claim 1, wherein: the first balance valve comprises a first check valve and a first overflow valve; an oil inlet of the first overflow valve is connected with a rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the first overflow valve is connected with a control oil port LB; a control oil port of the first overflow valve is connected with a control oil port LA; an oil inlet of the first check valve is connected with an oil outlet of the first overflow valve, and an oil outlet of the first check valve is connected with an oil inlet of the first overflow valve.
3. The balanced pressure self-protection hydraulic system of claim 2, wherein: the fourth balancing valve comprises a fourth one-way valve and a fourth overflow valve; an oil inlet of the fourth overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, an oil outlet of the fourth overflow valve is connected with a control oil port LB, and a control oil port of the fourth overflow valve is connected with a control oil port LA; an oil inlet of the fourth one-way valve is connected with an oil outlet of the fourth overflow valve, and an oil outlet of the fourth one-way valve is connected with a rodless cavity opening of the second variable amplitude oil cylinder.
4. The balanced pressure self-protection hydraulic system of claim 3, wherein: the second balance valve comprises a second check valve and a second overflow valve; the third balance valve comprises a third check valve and a third overflow valve; an oil inlet of the second overflow valve is connected with the rodless cavity port of the first variable amplitude oil cylinder, and an oil outlet of the second overflow valve is connected with an oil outlet of the third overflow valve; a control oil port of the second overflow valve is connected with a control oil port of the first overflow valve; an oil inlet of a third overflow valve is connected with a rodless cavity port of the second variable amplitude oil cylinder, and a control oil port of the third overflow valve is connected with a control oil port of a fourth overflow valve; an oil inlet of the second one-way valve is connected with an oil outlet of the second overflow valve, and an oil outlet of the second one-way valve is connected with an oil inlet of the second overflow valve; an oil inlet of the third one-way valve is connected with an oil outlet of the third overflow valve, and an oil outlet of the third one-way valve is connected with an oil inlet of the second overflow valve.
5. The balanced pressure self-protection hydraulic system of claim 4, wherein: the fifth balance valve comprises a fifth check valve and a fifth overflow valve; an oil inlet of a fifth overflow valve is connected with the other end of the first bidirectional motor, and an oil outlet of the fifth overflow valve is connected with a control oil port WB; a control oil port of the fifth overflow valve is connected with a control oil port WA; an oil inlet of the fifth one-way valve is connected with an oil outlet of the fifth overflow valve, and an oil outlet of the fifth one-way valve is connected with an oil inlet of the fifth overflow valve.
6. The balanced pressure self-protection hydraulic system of claim 5, wherein: the sixth balance valve comprises a sixth check valve and a sixth overflow valve; an oil inlet of the sixth overflow valve is connected with the other end of the second bidirectional motor, and an oil outlet of the sixth overflow valve is connected with a control oil port WB; a control oil port of the sixth overflow valve is connected with the control oil port WA; an oil inlet of the sixth one-way valve is connected with an oil outlet of the sixth overflow valve, and an oil outlet of the sixth one-way valve is connected with an oil inlet of the sixth overflow valve.
7. The balanced pressure self-protection hydraulic system of claim 1, wherein: the other end of first bi-directional motor is connected to the B mouth of first explosion-proof valve, and the F mouth of second explosion-proof valve is connected to the F mouth of first explosion-proof valve, and the other end of second bi-directional motor is connected to the B mouth of second explosion-proof valve, and the setting of F mouth that first choke valve is close to first explosion-proof valve is close to first throttle valve in the first explosion-proof valve, and the setting of F mouth that the second choke valve is close to the second explosion-proof valve is close to the second throttle valve in the second explosion-proof valve.
8. The balanced pressure self-protection hydraulic system of claim 1, wherein: the control oil ports LA, LB, WA and WB are connected with an oil tank through a hydraulic pump through reversing valves.
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