CN111503069A - Motor-driven hydraulic control system with flow adaptive distribution function - Google Patents
Motor-driven hydraulic control system with flow adaptive distribution function Download PDFInfo
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- CN111503069A CN111503069A CN202010297960.4A CN202010297960A CN111503069A CN 111503069 A CN111503069 A CN 111503069A CN 202010297960 A CN202010297960 A CN 202010297960A CN 111503069 A CN111503069 A CN 111503069A
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- 238000005315 distribution function Methods 0.000 title claims abstract description 20
- 230000003044 adaptive effect Effects 0.000 title claims description 12
- 239000003921 oil Substances 0.000 claims abstract description 167
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 65
- 238000013016 damping Methods 0.000 claims description 16
- 238000000034 method Methods 0.000 claims 1
- 230000000694 effects Effects 0.000 abstract description 6
- 230000033228 biological regulation Effects 0.000 abstract description 3
- 230000020169 heat generation Effects 0.000 abstract description 3
- 238000010438 heat treatment Methods 0.000 abstract description 2
- 230000006698 induction Effects 0.000 abstract 1
- 230000007246 mechanism Effects 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000003306 harvesting Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 235000013399 edible fruits Nutrition 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification 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
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
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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
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
-
- 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
- F15B13/08—Assemblies of units, each for the control of a single servomotor only
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
-
- 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
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
-
- 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 discloses a motor-driven hydraulic control system with a flow self-adaptive distribution function, which comprises a hydraulic oil tank, a first hydraulic motor and a second hydraulic motor, wherein the first hydraulic motor is connected with the second hydraulic motor through a hydraulic oil pipe; the first hydraulic motor is connected with a first motor control valve, a first flow regulator and a first motor rotation direction controller; the second hydraulic motor is connected with a second motor control valve, a second flow regulator and a second motor rotation direction controller; a third flow regulator is also included; the pressure induction ports of the three flow regulators are communicated with each other; when the load of one hydraulic motor is increased, the three flow regulators work in a matched mode, the oil inlet amount of the motor is increased, the oil inlet amount of the other motor is reduced, normal work is guaranteed, and when the load returns to be normal, the hydraulic motor returns to a normal hydraulic state under the matched regulation of the three flow regulators; the heating device has the characteristics of small heat generation and more energy saving; the control of a plurality of motors by one pump is realized, an electric control system is not needed, and the cost is relatively low; the scheme is easy to realize, and the operation effect is better.
Description
Technical Field
The invention relates to a hydraulic control system, in particular to a motor-driven hydraulic control system with a flow self-adaptive distribution function.
Background
In agricultural harvesting or construction machines, it is common to use two or more hydraulic motor-driven rotary mechanisms which have a kinematic relationship with respect to each other: for example, when a picking device (a rotating mechanism) in an agricultural harvesting machine is blocked (at the moment, the load is increased), a picking device (the rotating mechanism) of a header is required to automatically and properly reduce the speed (namely, the flow for driving a motor of the picking device is properly reduced), and meanwhile, the speed for driving the picking device is required to be properly increased (namely, the flow for driving the motor of the picking device is properly increased) so as to avoid the reduction of the working efficiency and even the flameout of an engine due to the sudden increase of the load; when the jam of the fruit picking device is solved, the rotation speed of the fruit picking device and the picking device is automatically restored to the preset rotation speed value. The traditional hydraulic system solution for realizing the function in the agricultural harvesting machine or the engineering machine is generally that two independent hydraulic pumps are arranged to respectively supply oil to two hydraulic motors, the flow rate flowing to the hydraulic motors is controlled by a proportional valve or a servo valve, and when a rotation speed sensor detects that the rotation speed of one motor is reduced, the proportional valve or the servo valve for controlling the motor is adjusted to increase the flow rate, and the proportional valve for controlling the other motor is adjusted to reduce the flow rate. In the traditional scheme, when the flow controlled by a proportional valve or a servo valve and flowing through the valve is reduced, redundant hydraulic oil of a hydraulic system overflows and returns to an oil tank through an overflow valve of the hydraulic system, so that the heating and power waste of the hydraulic system can be caused; the cost of sensors, controllers and the like in the control system is relatively high; the control strategy is relatively complicated, the control system is difficult to debug, and the operation effect is not ideal.
Disclosure of Invention
The invention aims to solve the technical problem of providing a motor-driven hydraulic control system with low cost and good regulation and control effect and having a flow self-adaptive distribution function.
In order to solve the technical problems, the technical scheme of the invention is as follows: the motor-driven hydraulic control system with the flow self-adaptive distribution function comprises a hydraulic oil tank, a first hydraulic motor and a second hydraulic motor, wherein the hydraulic oil tank is connected with an oil inlet main pipeline, a first oil inlet branch and a second oil inlet branch are respectively connected between the oil inlet main pipeline and the first hydraulic motor and between the oil inlet main pipeline and the second hydraulic motor, and the oil inlet main pipeline is connected with a hydraulic pump;
a first motor control valve, a first flow regulator and a first motor rotation direction controller are sequentially connected to the first oil inlet branch between the oil inlet main pipeline and the first hydraulic motor;
a second motor control valve, a second flow regulator and a second motor rotation direction controller are sequentially connected to the second oil inlet branch between the oil inlet main pipeline and the second hydraulic motor;
the oil inlet main pipeline is also connected with a third oil inlet branch pipeline, a third flow regulator is installed on the third oil inlet branch pipeline, and the third flow regulator is communicated with the hydraulic oil tank through an oil return pipeline;
and the pressure sensing port D of the first flow regulator, the pressure sensing port E of the second flow regulator and the pressure sensing port C of the third flow regulator are communicated with each other through a control oil way, and the tail end of the control oil way is communicated with the hydraulic oil tank through an overflow valve.
As a preferable technical solution, the first motor control valve is a two-position two-way electromagnetic proportional valve.
As a preferable technical solution, the first flow regulator is provided with three oil ports which are communicated with the outside, and the three oil ports are respectively a port P3, a port A3 and a pressure sensing port D, the first flow regulator comprises a first two-position two-way proportional valve which is connected between the port P3 and the port A3, a valve core non-return spring end of the first two-position two-way proportional valve is communicated with the port P3 through a control oil path, a first check valve is connected between a valve core return spring end of the first two-position two-way proportional valve and the port A3, and a hydraulic oil flowing direction of the first check valve is from the port A3 to a valve core return spring end of the first two-position two-way proportional valve; and a first damping valve is connected between the valve core reset spring end of the first two-position two-way proportional valve and the pressure sensing port D.
As a preferable technical solution, the first motor rotation direction controller includes a first clockwise needle control valve and a first counterclockwise needle control valve connected to the working oil port a9 and the working oil port B9 of the first hydraulic motor, respectively, and the P5 port of the first clockwise needle control valve and the P7 port of the first counterclockwise needle control valve are both connected to the first flow regulator through the first oil inlet branch.
As a preferable technical scheme, the first clockwise control valve and the first counterclockwise control valve are both two-position three-way electromagnetic valves, a P5 port of the first clockwise control valve is connected with the first oil inlet branch, an a5 port of the first clockwise control valve is connected with a working oil port a9 of the first hydraulic motor, and a T5 port of the first clockwise control valve is connected with the hydraulic oil tank through an oil return pipeline;
the P7 port of the first counterclockwise control valve is connected with the first oil inlet branch, the A7 port of the first counterclockwise control valve is connected with the B9 working oil port of the first hydraulic motor, and the T7 port of the first counterclockwise control valve is connected with the hydraulic oil tank through an oil return pipeline.
As a preferable technical solution, the second motor control valve is a two-position two-way electromagnetic proportional valve.
As a preferable technical solution, the second flow regulator is provided with three oil ports which are communicated with the outside, and the three oil ports are respectively a port P4, a port a4 and a pressure sensing port E, the second flow regulator comprises a second two-position two-way proportional valve which is connected between the port P4 and the port a4, a valve core non-return spring end of the second two-position two-way proportional valve is communicated with the port P4 through a control oil path, a second check valve is connected between a valve core return spring end of the second two-position two-way proportional valve and the port a4, and a hydraulic oil flowing direction of the second check valve is from the port a4 to a valve core return spring end of the second two-position two-way proportional valve; and a second damping valve is connected between the valve core reset spring end of the second two-position two-way proportional valve and the pressure sensing port E.
As a preferable technical solution, the second motor rotation direction controller includes a second counterclockwise control valve and a second clockwise control valve connected to the working oil port a10 and the working oil port B10 of the second hydraulic motor, respectively, and the P6 port of the second clockwise control valve and the P8 port of the second counterclockwise control valve are both connected to the second flow regulator through the second oil inlet branch.
As a preferable technical scheme, the second clockwise control valve and the second counterclockwise control valve are both two-position three-way electromagnetic valves, a P8 port of the second counterclockwise control valve is connected with the second oil inlet branch, an a8 port of the second counterclockwise control valve is connected with a working oil port a10 of the second hydraulic motor, and a T8 port of the second counterclockwise control valve is connected with the hydraulic oil tank through an oil return pipeline;
the port P6 of the second clockwise control valve is connected with the second oil inlet branch, the port A6 of the second clockwise control valve is connected with the working oil port B10 of the first hydraulic motor, and the port T6 of the second clockwise control valve is connected with the hydraulic oil tank through an oil return pipeline.
As a preferable technical scheme, the third flow regulator is provided with three oil ports which are communicated with the outside and are respectively a port P11, a port a11 and the pressure sensing port C, the third flow regulator comprises a three-position two-way proportional valve, a valve core non-return spring end of the three-position two-way proportional valve is communicated with the port P11 through a control oil path, and a third damping valve is connected between a valve core return spring end of the three-position two-way proportional valve and the port a 11.
By adopting the technical scheme, the motor-driven hydraulic control system with the flow self-adaptive distribution function comprises a hydraulic oil tank, a first hydraulic motor and a second hydraulic motor, wherein the hydraulic oil tank is connected with an oil inlet main pipeline, a first oil inlet branch and a second oil inlet branch are respectively connected between the oil inlet main pipeline and the first hydraulic motor and between the oil inlet main pipeline and the second hydraulic motor, and the oil inlet main pipeline is connected with a hydraulic pump; a first motor control valve, a first flow regulator and a first motor rotation direction controller are sequentially connected to the first oil inlet branch between the oil inlet main pipeline and the first hydraulic motor; a second motor control valve, a second flow regulator and a second motor rotation direction controller are sequentially connected to the second oil inlet branch between the oil inlet main pipeline and the second hydraulic motor; the oil inlet main pipeline is also connected with a third oil inlet branch pipeline, a third flow regulator is installed on the third oil inlet branch pipeline, and the third flow regulator is communicated with the hydraulic oil tank through an oil return pipeline; the pressure sensing port D of the first flow regulator, the pressure sensing port E of the second flow regulator and the pressure sensing port C of the third flow regulator are communicated with each other through a control oil way, and the tail end of the control oil way is communicated with the hydraulic oil tank through an overflow valve; when the load of one hydraulic motor is increased, the first flow regulator, the second flow regulator and the third flow regulator work in a matched mode to increase the oil inlet amount of the hydraulic motor and reduce the oil inlet amount of the other hydraulic motor so as to guarantee normal work, and when the load is recovered to be normal, the hydraulic motor is recovered to be in a normal hydraulic state under the matched regulation of the first flow regulator, the second flow regulator and the third flow regulator; the technical scheme has the characteristics of small heat generation and more energy saving; one pump can control a plurality of motors, an electric control system is not needed, and the cost is relatively low; the scheme is operable and easy to realize, and the operation effect is better.
Drawings
The drawings are only for purposes of illustrating and explaining the present invention and are not to be construed as limiting the scope of the present invention. Wherein:
FIG. 1 is a schematic diagram of an embodiment of the present invention;
FIG. 2 is a schematic diagram of an embodiment of the present invention controlling the operating states of two motors;
in the figure: 11-a hydraulic oil tank; 12-a hydraulic pump; 13-a filter; 14-an oil inlet main pipeline; 15-a first oil inlet branch; 16-a second oil inlet branch; 17-a third oil inlet branch; 2-a first hydraulic motor; 21-a first motor control valve; 22-a first flow regulator; 221-a two-position two-way proportional valve; 222-a first one-way valve; 223-a first damping valve; 23-a first clockwise control valve; 24-a first counter-clockwise control valve; 3-a second hydraulic motor; 31-a second motor control valve; 32-a second flow regulator; 321-second two-position two-way proportional valve; 322-a second one-way valve; 323-a second damping valve; 33-a second counter-clockwise control valve; 34-a second clockwise control valve; 4-a third flow regulator; no. 41-three two-position two-way proportional valve; 42-a third damping valve; 5-overflow valve.
Detailed Description
The invention is further illustrated below with reference to the figures and examples. In the following detailed description, certain exemplary embodiments of the present invention are described by way of illustration only. Needless to say, a person skilled in the art realizes that the described embodiments can be modified in various different ways without departing from the spirit and scope of the present invention. Accordingly, the drawings and description are illustrative in nature and not intended to limit the scope of the claims.
As shown in fig. 1, the motor-driven hydraulic control system with a flow adaptive distribution function includes a hydraulic oil tank 11, a first hydraulic motor 2, and a second hydraulic motor 3, where the hydraulic oil tank 11 is connected to an oil inlet main line 14, a first oil inlet branch 15 and a second oil inlet branch 16 are respectively connected between the oil inlet main line 14 and the first hydraulic motor 2 and the second hydraulic motor 3, and the oil inlet main line 14 is connected to a hydraulic pump 12;
a first motor control valve 21, a first flow regulator 22 and a first motor rotation direction controller are sequentially connected to the first oil inlet branch 15 between the oil inlet main pipeline 14 and the first hydraulic motor 2, the first motor rotation direction controller comprises a first clockwise control valve 23 and a first counterclockwise control valve 24 which are respectively connected with a working oil port A9 and a working oil port B9 of the first hydraulic motor 2, and a P5 port of the first clockwise control valve 23 and a P7 port of the first counterclockwise control valve 24 are both connected with the first flow regulator 22 through the first oil inlet branch 15;
a second motor control valve 31, a second flow regulator 32 and a second motor rotation direction controller are sequentially connected to the second oil inlet branch 16 between the oil inlet main pipeline 14 and the second hydraulic motor 3, the second motor rotation direction controller comprises a second counterclockwise needle control valve 33 and a second clockwise needle control valve 34 which are respectively connected with a working oil port A10 and a working oil port B10 of the second hydraulic motor 3, and a P6 port of the second clockwise needle control valve 34 and a P8 port of the second counterclockwise needle control valve 33 are both connected with the second flow regulator 32 through the second oil inlet branch 16;
the oil inlet main pipeline 14 is also connected with a third oil inlet branch 17, a third flow regulator 4 is installed on the third oil inlet branch 17, and the third flow regulator 4 is communicated with the hydraulic oil tank 11 through an oil return pipeline;
the pressure sensing port D of the first flow regulator 22, the pressure sensing port E of the second flow regulator 32, and the pressure sensing port C of the third flow regulator 4 are communicated with each other through a control oil path, and the end of the control oil path is communicated with the hydraulic oil tank 11 through a relief valve 5.
The first motor control valve 21 is a two-position two-way electromagnetic proportional valve. The first flow regulator 22 is provided with three oil ports which are communicated with the outside and are respectively a P3 port, an A3 port and a pressure sensing port D, the first flow regulator 22 comprises a first two-position two-way proportional valve 221 which is connected between the P3 port and the A3 port, a valve core non-return spring end of the first two-position two-way proportional valve 221 is communicated with the P3 port through a control oil path, a first check valve 222 is connected between a valve core return spring end of the first two-position two-way proportional valve 221 and the A3 port, and the hydraulic oil flowing direction of the first check valve 222 is from the A3 port to the valve core return spring end of the first two-position two-way proportional valve 221; a first damping valve 223 is connected between the valve core return spring end of the first two-position two-way proportional valve 221 and the pressure sensing port D.
The first clockwise control valve 23 and the first counterclockwise control valve 24 are two-position three-way electromagnetic valves, a P5 port of the first clockwise control valve 23 is connected with the first oil inlet branch 15, an a5 port of the first clockwise control valve 23 is connected with a working oil port a9 of the first hydraulic motor 2, and a T5 port of the first clockwise control valve 23 is connected with the hydraulic oil tank 11 through an oil return pipeline; the port P7 of the first counterclockwise control valve 24 is connected to the first oil inlet branch 15, the port a7 of the first counterclockwise control valve 24 is connected to the working oil port B9 of the first hydraulic motor 2, and the port T7 of the first counterclockwise control valve 24 is connected to the hydraulic oil tank 11 through an oil return line.
The second motor control valve 31 is a two-position two-way electromagnetic proportional valve. The second flow regulator 32 is provided with three oil ports which are communicated with the outside and are respectively a P4 port, an A4 port and the pressure sensing port E, the second flow regulator 32 comprises a second two-position two-way proportional valve 321 which is connected between the P4 port and the A4 port, a valve core non-return spring end of the second two-position two-way proportional valve 321 is communicated with the P4 port through a control oil path, a second check valve 322 is connected between a valve core return spring end of the second two-position two-way proportional valve 321 and the A4 port, and the hydraulic oil flowing direction of the second check valve 322 is from the A4 port to the valve core return spring end of the second two-position two-way proportional valve 321; and a second damping valve 323 is connected between the valve core return spring end of the second two-position two-way proportional valve 321 and the pressure sensing port E.
The second clockwise control valve 34 and the second counterclockwise control valve 33 are two-position three-way electromagnetic valves, a P8 port of the second counterclockwise control valve 33 is connected with the second oil inlet branch 16, an a8 port of the second counterclockwise control valve 33 is connected with a working oil port a10 of the second hydraulic motor 3, and a T8 port of the second counterclockwise control valve 33 is connected with the hydraulic oil tank 11 through an oil return pipeline; the port P6 of the second clockwise control valve 34 is connected to the second oil inlet branch 16, the port a6 of the second clockwise control valve 34 is connected to the working oil port B10 of the first hydraulic motor 2, and the port T6 of the second clockwise control valve 34 is connected to the hydraulic oil tank 11 through an oil return line.
The third flow regulator 4 is provided with three oil ports which are communicated with the outside and are respectively a P11 port, an A11 port and the pressure sensing port C, the third flow regulator 4 comprises a three-position two-way proportional valve 41, a valve core non-return spring end of the three-position two-way proportional valve 41 is communicated with the P11 port through a control oil path, and a third damping valve 42 is connected between the valve core return spring end of the three-position two-way proportional valve 41 and the A11 port. The oil inlet main pipeline 14 is also connected with a filter 13.
As shown in fig. 2, the electromagnet Y1 of the first motor control valve 21 is energized, the electromagnet Y2 of the second motor control valve 31 is energized, the port P1 of the first motor control valve 21 is communicated with the port a1, the port P2 of the second motor control valve 31 is communicated with the port a2, and the opening degree of the proportional valve is proportional to the energized value of the electromagnet; the electromagnet Y3 of the first clockwise control valve 23 is electrified, the electromagnet Y6 of the second counterclockwise control valve 33 is electrified, the port P5 of the first clockwise control valve 23 is communicated with the port A5, and the port P8 of the second counterclockwise control valve 33 is communicated with the port A8.
After the hydraulic oil from the outlet P of the hydraulic pump 12 passes through the filter 13, one of the oil paths reaches the first flow regulator 22 through the port P1 and the port a1 of the first motor control valve 21, the hydraulic oil acts on the end without the return spring of the first two-position two-way proportional valve 221 through the port P3 and the control oil path, and the acting force pushes the valve element of the first two-position two-way proportional valve 221 to move to enable the port P3 of the first flow regulator 22 to be communicated with the port A3 after interacting with the return spring of the valve element of the first two-position two-way proportional valve 221; the hydraulic oil from the port A3 of the first flow regulator 22 passes through the ports P5 and a5 of the first clockwise control valve 23 and then reaches the working port a9 of the first hydraulic motor 2; after the first hydraulic motor 2 is rotated by the hydraulic oil, the hydraulic oil flows out of the working oil port B9, passes through the port a7 and the port T7 of the first counterclockwise control valve 24, and returns to the hydraulic oil tank 11. In this state, the direction of the rotational motion output by the first hydraulic motor 2 is clockwise; if the electromagnet Y5 of the first counterclockwise control valve 24 is energized and the electromagnet Y3 of the first clockwise control valve 23 is not energized, the direction in which the first hydraulic motor 2 outputs rotational motion by the hydraulic oil is counterclockwise.
After the hydraulic oil from the outlet P of the hydraulic pump 12 passes through the filter 13, the second oil path reaches the second flow regulator 32 through the port P2 and the port a2 of the second motor control valve 31, the hydraulic oil passes through the port P4 and the control oil path, acts on the end without the return spring of the second two-position two-way proportional valve 321, and the acting force pushes the valve element of the second two-position two-way proportional valve 321 to move after interacting with the return spring of the valve element of the second two-position two-way proportional valve 321, so that the port P4 of the second flow regulator 32 is communicated with the port a 4; the hydraulic oil from the port a4 of the second flow regulator 32 passes through the ports P8 and A8 of the second counterclockwise control valve 33 and then reaches the working port a10 of the second hydraulic motor 3; the hydraulic oil makes the second hydraulic motor 3 rotate, and then flows out from the working oil port B10, passes through the port a6 and the port T6 of the second clockwise control valve 34, and returns to the hydraulic oil tank 11. In this state, the direction of the rotational motion output by the second hydraulic motor 3 is counterclockwise; if the electromagnet Y4 of the second clockwise control valve 34 is energized and the electromagnet Y6 of the second counterclockwise control valve 33 is not energized, the direction in which the second hydraulic motor 3 outputs the rotational motion by the hydraulic oil is clockwise.
The third oil path of the hydraulic oil from the outlet P of the hydraulic pump 12 after passing through the filter 13 reaches the inlet P11 of the third flow regulator 4, the hydraulic oil acts on the end without the return spring of the valve core of the three-position two-way proportional valve 41 through the control oil path, and the comparison result of the acting force, the acting force of the return spring of the valve core of the three-position two-way proportional valve 41 and the acting force acting on the end of the return spring of the valve core of the three-position two-way proportional valve 41 through the control oil path connected with the end determines the opening degree of the inlet P11 and the outlet A11 of the third flow regulator 4.
When the solenoid Y1 of the first motor control valve 21 is not energized and the solenoid Y2 of the second motor control valve 31 is not energized after the hydraulic pump 12 of the hydraulic system is started, all the hydraulic oil flowing out of the hydraulic pump 12 flows back to the hydraulic oil tank 11 through the P11 port and the a11 port of the third flow rate regulator 4. After the electromagnet Y1 of the first motor control valve 21 is electrified and the electromagnet Y2 of the second motor control valve 31 is electrified, the first hydraulic motor 2 and the second hydraulic motor 3 work smoothly and normally, and at the moment, if redundant hydraulic oil exists in the hydraulic system, the redundant hydraulic oil flows back to the hydraulic oil tank 11 through the P11 port and the A11 port of the third flow regulator 4. Compared with the scheme that the overflow valve overflows the hydraulic oil tank 11 in the traditional hydraulic system, the motor-driven hydraulic control system with the flow self-adaptive distribution function has the advantages of small heat productivity and obvious energy-saving effect.
If the load of the first hydraulic motor 2 suddenly increases (if the working mechanism is blocked) during the operation of the hydraulic system, the pressure signal responsible for the increase reaches the pressure sensing port D of the first flow regulator 22 from the port a3 of the first flow regulator 22 through the first check valve 222, the control oil passage, and the first damping valve 223. Then the pressure signal with increased load is divided into three paths: the first path reaches a pressure sensing port E of the second flow regulator 32, and then acts on a return spring end of a valve core of the second two-position two-way proportional valve 321 after passing through the second damping valve 323 and the control oil path, so that the valve core of the second two-position two-way proportional valve 321 moves for a certain displacement in a direction of reducing the opening degrees of the ports P4 and a4 of the second flow regulator 32, the flow rate of hydraulic oil flowing to the second hydraulic motor 3 is reduced, and the rotational motion speed output by the second hydraulic motor 3 is reduced; the second path of pressure signal with increased load reaches a pressure sensing port C of the third flow regulator 4 after passing through the control oil path, and then acts on a return spring end of a valve core of the three-position two-way proportional valve 41 after passing through the control oil path, so that the valve core of the three-position two-way proportional valve 41 moves for a certain displacement in a direction of reducing or even closing the opening degrees of the openings of the P11 and the a11 of the third flow regulator 4, the hydraulic oil flowing out of the hydraulic pump 12 flows to the first hydraulic motor 2 as much as possible, and the rotational motion speed output by the first hydraulic motor 2 is increased; and the third pressure signal with increased load reaches the inlet P12 of the overflow valve 5 after passing through the control oil path, and when the load signal value exceeds the set value of the overflow valve 5, the pressure signal is unloaded through the T12 of the overflow valve 5 and flows back to the hydraulic oil tank 11. When the situation that the load of the first hydraulic motor 2 is suddenly increased is solved, the third flow regulator 4, the first flow regulator 22 and the second flow regulator 32 automatically return to the original normal operating state, and the rotation speeds of the first hydraulic motor 2 and the second hydraulic motor 3 are automatically returned to the preset rotation speed values.
If the load of the second hydraulic motor 3 suddenly increases (if the working mechanism is blocked) during the operation of the hydraulic system, the increased pressure signal passes through the second check valve 322, the control oil passage, and the second damping valve 323 from the port a4 of the second flow regulator 32 and then reaches the pressure sensing port E of the second flow regulator 32. Then the pressure signal with increased load is divided into three paths: the first path reaches a pressure sensing port D of the first flow regulator 22, and then acts on a return spring end of a valve core of the first two-position two-way proportional valve 221 after passing through the first damping valve 223 and the control oil path, so that the valve core of the first two-position two-way proportional valve 221 moves for a certain displacement in a direction of reducing the opening degrees of the openings of the ports P3 and A3 of the first flow regulator 22, the flow rate of hydraulic oil flowing to the first hydraulic motor 2 is reduced, and the rotational motion speed output by the first hydraulic motor 2 is reduced; the second path of pressure signal with increased load reaches a pressure sensing port C of the third flow regulator 4 after passing through the control oil path, and then acts on a return spring end of a valve core of the three-position two-way proportional valve 41 after passing through the control oil path, so that the valve core of the three-position two-way proportional valve 41 moves for a certain displacement in a direction of reducing or even closing the opening degrees of the openings of the P11 and the a11 of the third flow regulator 4, the hydraulic oil flowing out of the hydraulic pump 12 flows to the second hydraulic motor 3 as much as possible, and the rotational motion speed output by the second hydraulic motor 3 is increased; and the third pressure signal with increased load reaches the inlet P12 of the overflow valve 5 after passing through the control oil path, and when the load signal value exceeds the set value of the overflow valve 5, the pressure signal is unloaded through the T12 of the overflow valve 5 and flows back to the hydraulic oil tank 11. When the situation that the load of the second hydraulic motor 3 is suddenly increased is solved, the third flow regulator 4, the first flow regulator 22 and the second flow regulator 32 automatically return to the original normal operating state, and the rotation speeds of the first hydraulic motor 2 and the second hydraulic motor 3 are automatically returned to the preset rotation speed values.
Compared with the common motor-driven hydraulic control system, the hydraulic control system with the flow self-adaptive distribution function has the characteristics of low heat generation and more energy conservation; one pump can control a plurality of motors, an electric control system is not needed, and the cost is relatively low; the scheme is operable and easy to realize, and the operation effect is better.
The foregoing shows and describes the general principles, essential features, and advantages of the invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only to illustrate the principle of the present invention, but that various changes and modifications may be made therein without departing from the spirit and scope of the present invention, which fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (10)
1. The motor-driven hydraulic control system with the flow self-adaptive distribution function comprises a hydraulic oil tank, a first hydraulic motor and a second hydraulic motor, wherein the hydraulic oil tank is connected with an oil inlet main pipeline, a first oil inlet branch and a second oil inlet branch are respectively connected between the oil inlet main pipeline and the first hydraulic motor and between the oil inlet main pipeline and the second hydraulic motor, and the oil inlet main pipeline is connected with a hydraulic pump; the method is characterized in that:
a first motor control valve, a first flow regulator and a first motor rotation direction controller are sequentially connected to the first oil inlet branch between the oil inlet main pipeline and the first hydraulic motor;
a second motor control valve, a second flow regulator and a second motor rotation direction controller are sequentially connected to the second oil inlet branch between the oil inlet main pipeline and the second hydraulic motor;
the oil inlet main pipeline is also connected with a third oil inlet branch pipeline, a third flow regulator is installed on the third oil inlet branch pipeline, and the third flow regulator is communicated with the hydraulic oil tank through an oil return pipeline;
and the pressure sensing port D of the first flow regulator, the pressure sensing port E of the second flow regulator and the pressure sensing port C of the third flow regulator are communicated with each other through a control oil way, and the tail end of the control oil way is communicated with the hydraulic oil tank through an overflow valve.
2. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 1, characterized in that: the first motor control valve is a two-position two-way electromagnetic proportional valve.
3. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 1, characterized in that: the first flow regulator is provided with three oil ports which are communicated with the outside and are respectively a P3 port, an A3 port and a pressure sensing port D, the first flow regulator comprises a first two-position two-way proportional valve connected between the P3 port and the A3 port, a valve core non-return spring end of the first two-position two-way proportional valve is communicated with the P3 port through a control oil path, a first check valve is connected between a valve core return spring end of the first two-position two-way proportional valve and the A3 port, and the hydraulic oil flowing direction of the first check valve is from the A3 port to the valve core return spring end of the first two-position two-way proportional valve; and a first damping valve is connected between the valve core reset spring end of the first two-position two-way proportional valve and the pressure sensing port D.
4. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 1, characterized in that: the first motor rotation direction controller comprises a working oil port A9 and a working oil port B9 which are connected with a first clockwise needle control valve and a first counterclockwise needle control valve respectively, and a P5 port of the first clockwise needle control valve and a P7 port of the first counterclockwise needle control valve are connected with the first flow regulator through a first oil inlet branch.
5. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 4, characterized in that: the first clockwise needle control valve and the first counterclockwise needle control valve are two-position three-way electromagnetic valves, a P5 port of the first clockwise needle control valve is connected with the first oil inlet branch, an A5 port of the first clockwise needle control valve is connected with a working oil port A9 of the first hydraulic motor, and a T5 port of the first clockwise needle control valve is connected with the hydraulic oil tank through an oil return pipeline;
the P7 port of the first counterclockwise control valve is connected with the first oil inlet branch, the A7 port of the first counterclockwise control valve is connected with the B9 working oil port of the first hydraulic motor, and the T7 port of the first counterclockwise control valve is connected with the hydraulic oil tank through an oil return pipeline.
6. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 1, characterized in that: the second motor control valve is a two-position two-way electromagnetic proportional valve.
7. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 1, characterized in that: the second flow regulator is provided with three oil ports which are communicated with the outside and are respectively a P4 port, an A4 port and a pressure sensing port E, the second flow regulator comprises a second two-position two-way proportional valve which is connected between the P4 port and the A4 port, a valve core non-return spring end of the second two-position two-way proportional valve is communicated with the P4 port through a control oil path, a second one-way valve is connected between a valve core return spring end of the second two-position two-way proportional valve and the A4 port, and the hydraulic oil flowing direction of the second one-way valve is from the A4 port to the valve core return spring end of the second two-position two-way proportional valve; and a second damping valve is connected between the valve core reset spring end of the second two-position two-way proportional valve and the pressure sensing port E.
8. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 1, characterized in that: the second motor rotation direction controller comprises a working oil port A10 and a working oil port B10 which are connected with a second counterclockwise needle control valve and a second clockwise needle control valve respectively, and a P6 port of the second clockwise needle control valve and a P8 port of the second counterclockwise needle control valve are connected with the second flow regulator through a second oil inlet branch.
9. The motor-driven hydraulic control system with flow adaptive distribution function according to claim 8, characterized in that: the second clockwise needle control valve and the second counterclockwise needle control valve are two-position three-way electromagnetic valves, a P8 port of the second counterclockwise needle control valve is connected with the second oil inlet branch, an A8 port of the second counterclockwise needle control valve is connected with a working oil port A10 of the second hydraulic motor, and a T8 port of the second counterclockwise needle control valve is connected with the hydraulic oil tank through an oil return pipeline;
the port P6 of the second clockwise control valve is connected with the second oil inlet branch, the port A6 of the second clockwise control valve is connected with the working oil port B10 of the first hydraulic motor, and the port T6 of the second clockwise control valve is connected with the hydraulic oil tank through an oil return pipeline.
10. The motor-driven hydraulic control system with a flow rate adaptive distribution function according to any one of claims 1 to 9, characterized in that: the third flow regulator is provided with three oil ports which are communicated with the outside and are respectively a P11 port, an A11 port and the pressure sensing port C, the third flow regulator comprises a three-position two-way proportional valve, a valve core non-return spring end of the three-position two-way proportional valve is communicated with the P11 port through a control oil path, and a third damping valve is connected between the valve core return spring end of the three-position two-way proportional valve and the A11 port.
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| JPH10274204A (en) * | 1997-03-31 | 1998-10-13 | Hitachi Constr Mach Co Ltd | Inertial body driving gear |
| JP2009167658A (en) * | 2008-01-15 | 2009-07-30 | Caterpillar Japan Ltd | Hydraulic control circuit of utility machine |
| CN110447393A (en) * | 2019-08-08 | 2019-11-15 | 山东五征集团有限公司 | Agricultural harvesting machinery ceding of Taiwan shape imitation hydraulic control system with pressure compensation |
| CN212615665U (en) * | 2020-04-16 | 2021-02-26 | 山东五征集团有限公司 | Motor-driven hydraulic control system with flow adaptive distribution function |
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2020
- 2020-04-16 CN CN202010297960.4A patent/CN111503069B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10274204A (en) * | 1997-03-31 | 1998-10-13 | Hitachi Constr Mach Co Ltd | Inertial body driving gear |
| JP2009167658A (en) * | 2008-01-15 | 2009-07-30 | Caterpillar Japan Ltd | Hydraulic control circuit of utility machine |
| CN110447393A (en) * | 2019-08-08 | 2019-11-15 | 山东五征集团有限公司 | Agricultural harvesting machinery ceding of Taiwan shape imitation hydraulic control system with pressure compensation |
| CN212615665U (en) * | 2020-04-16 | 2021-02-26 | 山东五征集团有限公司 | Motor-driven hydraulic control system with flow adaptive distribution function |
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