CN112249907A - Plunger pump composite control regulator and hoisting machinery - Google Patents
Plunger pump composite control regulator and hoisting machinery Download PDFInfo
- Publication number
- CN112249907A CN112249907A CN202011254349.XA CN202011254349A CN112249907A CN 112249907 A CN112249907 A CN 112249907A CN 202011254349 A CN202011254349 A CN 202011254349A CN 112249907 A CN112249907 A CN 112249907A
- Authority
- CN
- China
- Prior art keywords
- power
- differential pressure
- spring
- variable
- valve core
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/40—Applications of devices for transmitting control pulses; Applications of remote control devices
- B66C13/42—Hydraulic transmitters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/002—Hydraulic systems to change the pump delivery
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Automation & Control Theory (AREA)
- General Engineering & Computer Science (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention discloses a plunger pump composite control regulator, which comprises a variable power control valve and a variable differential pressure control valve which are mutually communicated, wherein the variable power control valve is communicated with a variable displacement pump, the variable differential pressure control valve is communicated with a hydraulic system, the variable power control valve comprises a power proportion electromagnet, a power spring and a power valve core, the variable differential pressure control valve comprises a differential pressure proportion electromagnet, a differential pressure spring and a constant current valve core, and a set current signal value is input to the power proportion electromagnet and the differential pressure proportion electromagnet to balance the thrust of the power proportion electromagnet, the thrust of the power spring and the thrust of a guide wheel mechanism so as to regulate the position of the power valve core and balance the thrust of the differential pressure proportion electromagnet, the thrust of the differential pressure spring and the hydraulic pressure of the system so as to regulate the position of. Effectively avoided low rotational speed operating mode easy flame-out's problem, the effectual insufficient problem of high rotational speed moment of torsion utilization of having solved improves compound action harmony and promotes the operating efficiency. The invention also discloses a hoisting machine comprising the regulator.
Description
Technical Field
The invention relates to the field of engineering equipment, in particular to a plunger pump composite control regulator. Furthermore, the invention also relates to a hoisting machine comprising the adjuster.
Background
In the existing hydraulic control system of hoisting machinery, under different working conditions, load difference and flow demand difference exist in each action of a main machine, so that the flow and pressure output by a plunger pump cannot meet system requirements in time. Referring to fig. 7, fig. 7 is an engine characteristic curve of an embodiment of the plunger pump composite control regulator provided in the present invention, and a conventional constant torque regulator cannot adapt to the engine torque characteristic requirement.
With the more mature matching of electric and hydraulic elements, the current electric control liquid driving becomes the development direction of engineering machinery, the electric control program can more effectively and simply exert the maximum efficiency of the hydraulic elements, and the deep matching of the electric control program and the hydraulic elements also plays a decisive role in the performance of the whole vehicle. When the crane operates in any combination or independent operation of main hoisting, auxiliary hoisting, stretching, amplitude variation and the like, the flow distribution of the execution mechanisms cannot be distributed in proportion due to different loads, the flow and speed difference among different execution mechanisms is large, the coordination of the combination action is poor, and the labor intensity and the working efficiency of an operator are affected. In addition, according to survey statistics, the crane works at a waiting speed for more than 50% of time, the traditional engine only works at about 1500rpm for about 70% of time during hoisting, the traditional constant power regulator for the plunger pump can cause the engine to be easy to stall under the working condition of low rotating speed, and the energy is wasted due to insufficient torque utilization under the working condition of high rotating speed.
Therefore, how to provide a plunger pump compound control regulator which overcomes the above problems is a technical problem which needs to be solved by the technical personnel in the field at present.
Disclosure of Invention
The invention aims to provide a plunger pump composite control regulator, which solves the problem that the load flow demand is inconsistent with the actual working condition demand caused by invariable differential pressure of a hydraulic system through a variable power control valve and a variable differential pressure control valve, and simultaneously solves the problems that the engine is easy to be flamed out under the low-rotating-speed working condition and the torque is not sufficiently utilized under the high-rotating-speed working condition. It is a further object of the present invention to provide a hoisting machine comprising the above-mentioned adjuster.
In order to solve the technical problems, the invention provides a plunger pump composite control regulator, which comprises a variable power control valve and a variable differential pressure control valve which are mutually communicated, wherein the variable power control valve is communicated with a variable pump, the variable differential pressure control valve is communicated with a hydraulic system, a guide wheel mechanism is arranged at the outlet of the variable pump, the guide wheel mechanism is connected with the variable power control valve through a shift lever and transmits thrust, the variable power control valve comprises a power proportion electromagnet, a power spring and a power valve core, the variable differential pressure control valve comprises a differential pressure proportion electromagnet, a differential pressure spring and a constant current valve core, and set current signal values are input into the power proportion electromagnet and the differential pressure proportion electromagnet to balance the thrust of the power proportion electromagnet, the thrust of the power spring and the thrust of the guide wheel mechanism so as to regulate the position of the power valve core and to ensure that the thrust of the differential pressure proportion electromagnet is balanced, The thrust of the differential pressure spring is balanced with the system hydraulic pressure so as to adjust the position of the constant flow valve core.
Preferably, the variable-displacement hydraulic control valve comprises a valve body, a power cavity and a pressure difference cavity are arranged in the valve body in parallel, the power cavity is communicated with the pressure difference cavity through a connecting cavity, the power cavity is communicated with a variable-displacement pump outlet, the pressure difference cavity is communicated with an oil supply port and a feedback oil port of a hydraulic system, a power proportional electromagnet is installed at a driving port of the power cavity, a power spring and a power valve core are installed in the power cavity, a deflector rod extends into the power cavity, the pressure difference proportional electromagnet is installed at the driving port of the pressure difference cavity, and the pressure difference spring and a flow valve constant core are installed in the.
Preferably, one end of the power valve core is connected with the power proportional electromagnet, the other end of the power valve core abuts against one side face of the tail end of the shifting lever through a thimble, the other side face of the tail end of the shifting lever abuts against the power spring, and the power proportional electromagnet drives the power valve core to move and compress the power spring.
Preferably, a power end cover is installed at an adjusting port of the power cavity, a power adjusting screw is installed on the power end cover, and the inner end of the power adjusting screw abuts against the power spring.
Preferably, a return spring is arranged between the power valve core and the power proportion electromagnet.
Preferably, a valve sleeve is arranged in the pressure difference cavity, a push rod is arranged in the valve sleeve, the pressure difference proportion electromagnet is connected with one end of the push rod, the other end of the push rod is connected with one end of the constant current valve core, the other end of the constant current valve core is abutted against the pressure difference spring, the pressure difference proportion electromagnet drives the push rod and the constant current valve core to move and compress the pressure difference spring, and the feedback oil port and the oil supply port are respectively located in the pressure difference cavity where the constant current valve core and the push rod are located.
Preferably, a pressure difference end cover is installed at an adjusting port of the pressure difference cavity, a pressure difference adjusting screw is installed on the pressure difference end cover, and the inner end of the pressure difference adjusting screw abuts against the pressure difference spring.
Preferably, the differential pressure spring comprises two sets of springs nested together.
Preferably, the power spring and the differential pressure spring are provided at both ends thereof with paired spring seats.
The invention provides hoisting machinery comprising the plunger pump composite control regulator.
The invention provides a plunger pump composite control regulator, which comprises a variable power control valve and a variable differential pressure control valve which are mutually communicated, wherein the variable power control valve is communicated with a variable pump, the variable differential pressure control valve is communicated with a hydraulic system, a guide wheel mechanism is arranged at the outlet of the variable pump, the guide wheel mechanism is connected with the variable power control valve through a deflector rod and transmits thrust, the variable power control valve comprises a power proportional electromagnet, a power spring and a power valve core, the variable differential pressure control valve comprises a differential pressure proportional electromagnet, a differential pressure spring and a constant current valve core, and set current signal values are input to the power proportional electromagnet and the differential pressure proportional electromagnet, so that the thrust of the power proportional electromagnet, the thrust of the power spring and the thrust of the guide wheel mechanism are balanced to regulate the position of the power valve core, balance the thrust of the differential pressure proportional electromagnet, the thrust of the differential pressure spring and the.
The variable power control valve and the variable differential pressure control valve are utilized, current control can be carried out on the relevant proportional electromagnets only through a preset electric control program, when the engine is in a low-rotation-speed working condition, the power proportional electromagnets can compensate thrust to enable the power valve core to further compress the power spring, the torque starting point is reduced, the overall torque of the final variable pump is reduced, and the problem that flameout is easy under the low-rotation-speed working condition is effectively avoided; when the engine is in a high-rotating-speed working condition, the power proportion electromagnet can reduce the compensation thrust to enable the power valve core to weaken and compress the power spring, the torque starting point is increased, the integral torque of the variable displacement pump is increased, and the problem of insufficient utilization of high-rotating-speed torque is effectively solved. Meanwhile, when the host is in a standby working condition, the differential pressure at two ends of the constant flow valve core is overlarge, and the differential pressure proportion electromagnet can compensate thrust to reduce the differential pressure of the constant flow valve core so as to reduce the pressure loss of the system; when the main machine is in other composite working conditions, the pressure difference at the two ends of the constant flow valve core is too small, and the pressure difference proportion electromagnet can also reduce the compensation thrust to enable the constant flow valve core to be always maintained at a critical working position, so that the composite action coordination is improved, and the working efficiency is improved.
The invention also provides a hoisting machine comprising the adjuster, and the hoisting machine has the technical effects, so the hoisting machine has the same technical effects, and the detailed description is omitted.
Drawings
FIG. 1 is a hydraulic schematic of one embodiment of a compound control regulator for a plunger pump provided in accordance with the present invention;
FIG. 2 is a schematic structural diagram of one embodiment of a compound control regulator for a plunger pump according to the present invention;
FIG. 3 is a cross-sectional view of one embodiment of a compound control regulator for a plunger pump provided in accordance with the present invention;
FIG. 4 is a high speed torque control curve for one embodiment of a plunger pump compound control regulator provided in accordance with the present invention;
FIG. 5 is a low speed torque control curve for one embodiment of a plunger pump compound control regulator provided in accordance with the present invention;
FIG. 6 is a differential pressure control curve for one embodiment of a compound control regulator for a plunger pump provided in accordance with the present invention;
FIG. 7 is an engine map of one embodiment of a plunger pump compound control regulator provided by the present invention.
Detailed Description
The core of the invention is to provide a plunger pump composite control regulator, which solves the problem that the load flow demand is inconsistent with the actual working condition demand caused by invariable differential pressure of a hydraulic system through a variable power control valve and a variable differential pressure control valve, and simultaneously solves the problems that the engine is easy to be flamed out under the low-rotating-speed working condition and the torque is not sufficiently utilized under the high-rotating-speed working condition. Another core of the present invention is to provide a hoisting machine comprising the above-mentioned adjuster.
In order that those skilled in the art will better understand the disclosure, the invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
Referring to fig. 1 to 3, fig. 1 is a hydraulic schematic diagram of an embodiment of a compound control regulator of a plunger pump according to the present invention; FIG. 2 is a schematic structural diagram of one embodiment of a compound control regulator for a plunger pump according to the present invention; FIG. 3 is a cross-sectional view of one embodiment of a compound control regulator for a plunger pump provided in accordance with the present invention.
The invention provides a plunger pump composite control regulator, which comprises a variable power control valve 1 and a variable pressure difference control valve 2 which are mutually communicated, wherein the variable power control valve 1 is communicated with a variable pump 3 through a pipeline, the variable pressure difference control valve 2 is communicated with a hydraulic system through a pipeline, an outlet of the variable pump 3 is provided with a guide wheel mechanism 4, the guide wheel mechanism 4 is connected with the variable power control valve 1 through a shift lever 5 and transmits thrust, namely, the pressure at the outlet of the variable pump 3 is transmitted to the variable power control valve 1 through the guide wheel mechanism 4 and the shift lever 5, the variable power control valve 1 comprises a power proportion electromagnet 11, a power spring 12 and a power valve core 13, the variable pressure difference control valve 2 comprises a differential pressure proportion electromagnet 21, a differential pressure spring 22 and a constant flow valve core 23, and the priority of the variable power control valve 1 is higher than that of the variable pressure difference control valve 2. Under different working conditions, the device inputs a set current signal value to the power proportion electromagnet 11 and the differential pressure proportion electromagnet 21 according to a preset electric control program, pushes the power proportion electromagnet 11, balances the thrust of the power proportion electromagnet 11, the thrust of the power spring 12 and the thrust of the guide wheel mechanism 4, adjusts the position of the power valve core 13, enables the power valve core 13 to work stably, controls the hydraulic oil output by the variable power control valve 1, and further controls the power of a system. Meanwhile, the differential pressure proportion electromagnet 21 is pushed, so that the thrust of the differential pressure proportion electromagnet 21, the thrust of the differential pressure spring 22 and the system hydraulic pressure are balanced, the position of the constant flow valve core 23 is adjusted, the constant flow valve core 23 is always in a critical working state, the hydraulic oil output by the variable differential pressure control valve 2 is controlled, and the differential pressure of the system is further controlled.
By utilizing the variable power control valve 1 and the variable differential pressure control valve 2, current control can be carried out on the related proportional electromagnets only through a preset electric control program, when the engine is in a low-rotation-speed working condition, the power proportional electromagnet 11 can compensate thrust to further compress the power spring 12 by the power valve core 13, the torque starting point is reduced, the overall torque of the variable pump 3 is reduced, and the problem that the variable pump is easy to extinguish in the low-rotation-speed working condition is effectively avoided; when the engine is in a high-rotating-speed working condition, the power proportion electromagnet 11 can reduce the compensation thrust to enable the power valve core 13 to weaken and compress the power spring 12, the torque starting point is increased, finally, the integral torque of the variable displacement pump 3 is increased, and the problem of insufficient utilization of high-rotating-speed torque is effectively solved. Meanwhile, when the main engine is in a standby working condition, the pressure difference between two ends of the constant flow valve core 23 is overlarge, and the pressure difference proportion electromagnet 21 can compensate thrust to reduce the pressure difference of the constant flow valve core 23 so as to reduce the pressure loss of the system; when the main machine is in other composite working conditions, the pressure difference at the two ends of the constant flow valve core 23 is too small, and the pressure difference proportion electromagnet 21 can also reduce the compensation thrust to enable the constant flow valve core 23 to be always maintained at the critical working position, so that the composite action coordination is improved, and the working efficiency is improved.
In the plunger pump composite control regulator provided by the embodiment of the invention, the valve body 6 is arranged, the power cavity and the pressure difference cavity are arranged in the valve body 6 in parallel, specifically, two transversely extending through holes can be arranged in the valve body 6 up and down, openings at two ends of the through holes are respectively positioned at two sides of the valve body 6, the two through holes are respectively the power cavity and the pressure difference cavity, wherein two ends of the through holes are respectively a driving port and an adjusting port, and the driving ports of the two through holes can be positioned at the same side of the valve body 6 or at different sides. Furthermore, a longitudinally extending hole is arranged between the power cavity and the differential pressure cavity and used as a connecting cavity 61 for communicating the power cavity and the differential pressure cavity, meanwhile, a plurality of oil duct pipelines are arranged on the valve body 6, the power cavity is communicated with an outlet of the variable pump 3, the differential pressure cavity is communicated with an oil supply port and a feedback oil port of the hydraulic system, hydraulic oil sequentially passes through the variable pump 3, the variable power control valve 1 and the variable differential pressure control valve 2 to enter the hydraulic system, and can also flow back to the variable differential pressure control valve 2 through the feedback oil port.
The power proportion electromagnet 11 is installed at a driving port of a power cavity, a power spring 12 and a power valve core 13 are installed in the power cavity, the shifting rod 5 extends into the power cavity, furthermore, one end of the power valve core 13 is connected with the power proportion electromagnet 11, the other end of the power valve core 13 abuts against one side face of the tail end of the shifting rod 5 through the ejector pin 14, the other side face of the tail end of the shifting rod 5 abuts against the power spring 12, the power proportion electromagnet 11 drives the power valve core 13 to move, the ejector pin 14 and the shifting rod 5 can be sequentially pushed, and then the power spring 12 is compressed. A return spring 17 may also be provided between the power spool 13 and the power proportional solenoid 11 to assist in resetting the power spool 13. Namely, the variable power control valve 1 comprises a power proportion electromagnet 11, a return spring 17, a power valve core 13, an ejector pin 14, a shift lever 5 and a power spring 12 which are arranged in sequence.
The variable power control method comprises the following steps: under different working conditions, a corresponding current signal value is given to the power proportional electromagnet 11 according to a preset electric control program, the thrust of the power proportional electromagnet 11 is transmitted to the power valve core 13, and the guide wheel mechanism 4 senses the outlet pressure of the variable pump 3 and finally reflects the outlet pressure to the tail end of the deflector rod 5; the thrust of the power proportional electromagnet 11 is transmitted to the power valve core 13 and is finally reflected to the right end face of the tail end of the shift lever 5 by the ejector pin 14, and the elastic force of the power spring 12 is reflected to the left end face of the tail end of the shift lever 5; finally, the thrust of the power proportion electromagnet 11, the thrust of the guide wheel mechanism 4 and the elastic force of the power spring 12 are balanced, so that the power valve core 13 stably works after moving to a preset position.
The differential pressure proportion electromagnet 21 is installed at a driving port of the differential pressure chamber, and the differential pressure spring 22 and the constant flow valve core 23 are installed in the differential pressure chamber. Furthermore, a valve sleeve 24 is fixed in the pressure difference cavity, a push rod 25 is arranged in the valve sleeve 24, the pressure difference proportion electromagnet 21 is connected with one end of the push rod 25, the other end of the push rod 25 is connected with one end of the constant flow valve core 23, the other end of the constant flow valve core 23 is abutted against the pressure difference spring 22, the pressure difference proportion electromagnet 21 drives the push rod 25 to move in the valve sleeve 24 and pushes the constant flow valve core 23 to move, the pressure difference spring 22 is further compressed, and meanwhile, the feedback oil port and the oil supply port are respectively located at the position of the constant flow valve core 23 and the position of the push rod. Wherein, pressure differential spring 22 includes two sets of springs of suit, and two sets of spring diameters are different promptly, and the suit that the diameter is big is in the periphery that the diameter is little, realizes multistage compression regulation. Namely, the variable differential pressure control valve 2 comprises a differential pressure proportion electromagnet 21, a push rod 25, a constant flow valve core 23 and a differential pressure spring 22 which are arranged in sequence.
The control method of the variable pressure difference comprises the following steps: under different working conditions, a corresponding current signal value is given to the differential pressure proportion electromagnet 21 according to a preset electric control program, the thrust of the differential pressure proportion electromagnet 21 acts on the constant flow valve core 23 through the push rod 25, the push rod 25 has a difference of two step areas so as to sense the pressure of the hydraulic system, the constant flow valve core 23 senses the load pressure of the hydraulic system through a feedback oil port, and finally the thrust of the differential pressure proportion electromagnet 21, the hydraulic pressure borne by the push rod 25, the hydraulic pressure borne by the constant flow valve core 23 and the elastic force of the differential pressure spring 22 are balanced, so that the constant flow valve core 23 is always in a critical working state after moving to a preset position.
Preferably, a power end cover 15 is installed at the adjusting port of the power cavity, a power adjusting screw 16 is installed on the power end cover 15, and the inner end of the power adjusting screw 16 abuts against the power spring 12. The adjusting port of the pressure difference cavity is provided with a pressure difference end cover 26, the pressure difference end cover 26 is provided with a pressure difference adjusting screw 27, and the inner end of the pressure difference adjusting screw 27 is propped against the pressure difference spring 22. By rotating the power adjusting screw 16 and the differential pressure adjusting screw 27, the compression degree of the power spring 12 and the differential pressure spring 22 can be adjusted, and further the initial power starting point, the differential pressure adjusting parameter and the like can be adjusted. In order to ensure the sealing effect, structures such as sealing rings can be arranged at corresponding positions of all the parts.
In the plunger pump compound control regulator provided in each of the above embodiments, pairs of spring seats are provided at both ends of the power spring 12 and the differential pressure spring 22, so as to facilitate installation and use of the springs.
Referring to fig. 4 to 7, fig. 4 is a high rotational speed torque control curve of an embodiment of the plunger pump composite control regulator of the present invention; FIG. 5 is a low speed torque control curve for one embodiment of a plunger pump compound control regulator provided in accordance with the present invention; FIG. 6 is a differential pressure control curve for one embodiment of a compound control regulator for a plunger pump provided in accordance with the present invention; FIG. 7 is an engine map of one embodiment of a plunger pump compound control regulator provided by the present invention.
According to fig. 4 and 5, the initial setting requirements for the control of power are as follows: controlling the power of a starting point to be 28KW, the rotating speed to be 800rpm and the control current to be 200 mA; the power of the control terminal point is 88KW, the rotating speed is 2300rpm, and the control current is 600 mA. By calculation of formula
Qv is flow, η t is total efficiency, a power starting point of 28KW/88KW can be obtained, when the area difference of the valve element of the guide wheel mechanism 4 is determined after the maximum thrust of the power proportional electromagnet 11 is determined, the thrust of the power proportional electromagnet x moment arm L1+ the thrust of the guide wheel mechanism x moment arm L2 is equal to the power spring force x moment arm L1. When the input current of the proportional electromagnet is 200 mA-600 mA, the power is reduced from 88KW to 28KW, namely, the function of reducing the power by increasing the current is realized, and the problems that the engine is easy to flameout under the low-rotating-speed working condition and the torque is not sufficiently utilized under the high-rotating-speed working condition can be effectively solved.
According to fig. 6, the initial setting requirements for the control of the pressure difference are as follows: controlling the pressure difference delta p of the starting point to be 25bar and controlling the current to be 200 mA; the pressure difference deltap at the control end point is 12bar, and the current is controlled to be 600 mA. When the constant flow valve core is in a critical working state, the elastic force of a differential pressure spring is (variable pump outlet pressure p-hydraulic system feedback pressure PLs) multiplied by the sectional area of the constant flow valve core and the thrust of the differential pressure proportion electromagnet, namely, the thrust of the differential pressure proportion electromagnet is increased due to the increase of current, so that the differential pressure is reduced.
When the system is in a standby working condition, the throttle valve of the hydraulic system is fully closed, and at the moment, the current can be increased through an electric control program, so that the pressure difference delta p is reduced, and finally the pressure loss of the system is reduced; when the host enters a composite working condition, the priority of the power section is higher than that of the constant-current section, so that the flow of the variable pump is correspondingly reduced according to a pressure difference classical formula
The pressure difference is inversely proportional to the flow, w is the width of the valve port, and x is the opening of the valve port, so that the pressure difference delta p is reduced; because the initial spring is set, the constant-flow valve core tends to deviate from a critical working position, so that the constant-flow valve core cannot be in a standby state at any time and needs a certain reaction stroke; at the moment, a current signal can be given to the differential pressure proportion electromagnet according to an electric control program, the thrust of the differential pressure proportion electromagnet acts on the constant current valve core through the push rod, and finally the thrust of the differential pressure proportion electromagnet, the hydraulic pressure borne by the push rod, the hydraulic pressure borne by the constant flow valve and the elastic force of the differential pressure spring are balanced to enable the constant flow valve to be always in a critical working state, so that the composite action coordination can be effectively improved, and the working efficiency is improved. Or applicability adjustment of various data parameters, are within the scope of the invention.
In addition to the plunger pump composite control regulator, the embodiments of the present invention also provide a hoisting machine including the plunger pump composite control regulator, and the structures of other parts of the hoisting machine refer to the prior art and are not described herein again.
The plunger pump composite control regulator and the hoisting machinery provided by the invention are described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the method and its core concepts. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.
Claims (10)
1. A plunger pump composite control regulator is characterized by comprising a variable power control valve (1) and a variable differential pressure control valve (2) which are communicated with each other, wherein the variable power control valve (1) is communicated with a variable pump (3), the variable differential pressure control valve (2) is communicated with a hydraulic system, an outlet of the variable pump (3) is provided with a guide wheel mechanism (4), the guide wheel mechanism (4) is connected with the variable power control valve (1) through a shift lever (5) and transmits thrust, the variable power control valve (1) comprises a power proportional electromagnet (11), a power spring (12) and a power valve core (13), the variable differential pressure control valve (2) comprises a differential pressure proportional electromagnet (21), a differential pressure spring (22) and a constant flow valve core (23), and set current signal values are input into the power proportional electromagnet (11) and the differential pressure proportional electromagnet (21), and balancing the thrust of the power proportional electromagnet (11), the thrust of the power spring (12) and the thrust of the guide wheel mechanism (4) to adjust the position of the power valve core (13), and balancing the thrust of the differential pressure proportional electromagnet (21), the thrust of the differential pressure spring (22) and the system hydraulic pressure to adjust the position of the constant flow valve core (23).
2. The plunger pump composite control regulator according to claim 1, characterized by comprising a valve body (6), wherein a power cavity and a pressure difference cavity are arranged in the valve body (6) in parallel, the power cavity is communicated with the pressure difference cavity through a connecting cavity (61), the power cavity is communicated with an outlet of the variable displacement pump (3), the pressure difference cavity is communicated with an oil supply port and a feedback oil port of a hydraulic system, the power proportional electromagnet (11) is installed at a driving port of the power cavity, the power spring (12) and the power valve core (13) are installed in the power cavity, the deflector rod (5) extends into the power cavity, the pressure difference proportional electromagnet (21) is installed at the driving port of the pressure difference cavity, and the pressure difference spring (22) and the constant current valve core (23) are installed in the pressure difference cavity.
3. The plunger pump composite control regulator according to claim 2, characterized in that one end of the power valve core (13) is connected with the power proportional electromagnet (11), the other end of the power valve core (13) is abutted against one side surface of the tail end of the shift lever (5) through an ejector pin (14), the other side surface of the tail end of the shift lever (5) is abutted against the power spring (12), and the power proportional electromagnet (11) drives the power valve core (13) to move and compress the power spring (12).
4. The plunger pump composite control regulator as claimed in claim 3, wherein the regulating port of the power chamber is provided with a power end cover (15), the power end cover (15) is provided with a power regulating screw (16), and the inner end of the power regulating screw (16) is abutted against the power spring (12).
5. The plunger pump compound control regulator according to claim 4, characterized in that a return spring (17) is arranged between the power spool (13) and the power proportional solenoid (11).
6. The plunger pump composite control regulator as recited in claim 2, wherein a valve sleeve (24) is disposed in the differential pressure chamber, a push rod (25) is disposed in the valve sleeve (24), the differential pressure proportional electromagnet (21) is connected to one end of the push rod (25), the other end of the push rod (25) is connected to one end of the constant flow valve core (23), the other end of the constant flow valve core (23) abuts against the differential pressure spring (22), the differential pressure proportional electromagnet (21) drives the push rod (25) and the constant flow valve core (23) to move and compress the differential pressure spring (22), and the feedback oil port and the oil supply port are respectively located in the differential pressure chamber where the constant flow valve core (23) and the push rod (25) are located.
7. The plunger pump composite control regulator as claimed in claim 6, wherein a pressure difference end cover (26) is mounted at the regulating port of the pressure difference cavity, a pressure difference regulating screw (27) is mounted on the pressure difference end cover (26), and the inner end of the pressure difference regulating screw (27) is abutted against the pressure difference spring (22).
8. The plunger pump compound control regulator of claim 7, wherein the differential pressure spring (22) comprises two sets of springs nested together.
9. Plunger pump compound control regulator according to any of claims 1 to 8, characterized in that the power spring (12) and the differential pressure spring (22) are provided with pairs of spring seats at both ends.
10. Hoisting machine, characterized in that it comprises a plunger pump complex control regulator according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011254349.XA CN112249907A (en) | 2020-11-11 | 2020-11-11 | Plunger pump composite control regulator and hoisting machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011254349.XA CN112249907A (en) | 2020-11-11 | 2020-11-11 | Plunger pump composite control regulator and hoisting machinery |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112249907A true CN112249907A (en) | 2021-01-22 |
Family
ID=74266998
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011254349.XA Pending CN112249907A (en) | 2020-11-11 | 2020-11-11 | Plunger pump composite control regulator and hoisting machinery |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112249907A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114508483A (en) * | 2022-02-28 | 2022-05-17 | 华侨大学 | Power adjusting system and method for hydraulic pump |
-
2020
- 2020-11-11 CN CN202011254349.XA patent/CN112249907A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114508483A (en) * | 2022-02-28 | 2022-05-17 | 华侨大学 | Power adjusting system and method for hydraulic pump |
| CN114508483B (en) * | 2022-02-28 | 2023-05-16 | 华侨大学 | Power adjusting system and adjusting method of hydraulic pump |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0228817B1 (en) | Hydraulic control apparatus for stepless transmission | |
| CN101871477B (en) | Intermediate-pressure control two-position variable axial plunger hydraulic motor | |
| CN109469594B (en) | Continuous pressure regulating electro-hydraulic proportional axial plunger variable pump for aircraft hydraulic system | |
| CN102261351A (en) | Simple proportional load sensitive hydraulic system | |
| CN109210187B (en) | Hydraulic control system and method for double-clutch transmission and automobile | |
| CN105179221A (en) | Constant power adjusting system for duplex axial plunger pump and application of constant power adjusting system | |
| CN112249907A (en) | Plunger pump composite control regulator and hoisting machinery | |
| CN205779974U (en) | A kind of novel electro-hydraulic proportional multi-way valve | |
| US20140060034A1 (en) | Electro-Hydraulic Control Design for Pump Discharge Pressure Control | |
| CN104728431A (en) | Electromagnetic control valve with adjustable voltage and speed adjusting variable torque transmission device hydraulic system adopting same | |
| CN204553818U (en) | Pressure-adjustable solenoid electric valve and adopt its speed governing bending moment transmission device hydraulic system | |
| CN214031452U (en) | Plunger pump composite control regulator and hoisting machinery | |
| KR0149708B1 (en) | Apparatus of controlling rotating torque | |
| US5243820A (en) | Hydraulic circuit with compensator valve biased with highest pressure acting on actuators | |
| JPS5888480A (en) | Input control for hydraulic pump driven by prime mover | |
| US11280357B1 (en) | Hydraulic variable pump set and excavator | |
| CN112283186B (en) | Hydraulic control system of automatic transmission and control method thereof | |
| CN210344387U (en) | Variable differential pressure flow divider valve based on damping bridge circuit and hydraulic control system | |
| JPH0617761A (en) | Power controller for at least two variable discharge hydraulic pump | |
| CN108516467B (en) | The hydraulic control system and hoisting machinery of hoisting machinery | |
| CN2597697Y (en) | Hydraulic plunger variable motor regulating controller | |
| CN114623118B (en) | Load-sensitive hydraulic transmission system, method and engineering mechanical device thereof | |
| CN213419538U (en) | Throttling induction type power control structure of plunger pump | |
| CN220353990U (en) | Power control valve and hydraulic pump | |
| CN114046206B (en) | Closed-loop regulation control device for oil supply selection and switching of combined pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |