CN104329306A - Hydraulic control system and method as well as pump - Google Patents
Hydraulic control system and method as well as pump Download PDFInfo
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- CN104329306A CN104329306A CN201410607037.0A CN201410607037A CN104329306A CN 104329306 A CN104329306 A CN 104329306A CN 201410607037 A CN201410607037 A CN 201410607037A CN 104329306 A CN104329306 A CN 104329306A
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- oil
- pumping
- reversing
- cylinder
- valve group
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- 238000000034 method Methods 0.000 title claims abstract description 17
- 238000005086 pumping Methods 0.000 claims abstract description 228
- 239000003921 oil Substances 0.000 claims description 534
- 239000010720 hydraulic oil Substances 0.000 claims description 103
- 230000001960 triggered effect Effects 0.000 claims description 9
- 238000013459 approach Methods 0.000 claims description 4
- 238000006073 displacement reaction Methods 0.000 abstract description 5
- 230000003139 buffering effect Effects 0.000 abstract 2
- 238000010586 diagram Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- 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
-
- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/16—Characterised by the construction of the motor unit of the straight-cylinder type of the telescopic type
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to a hydraulic control system. The hydraulic control system comprises an oscillating oil cylinder, a first pressure oil source, a pumping main oil cylinder, an oscillating oil cylinder reversing valve set, a pumping system combination and a reversing buffering valve set, wherein the oscillating oil cylinder reversing valve set is used for reversing a piston of the oscillating oil cylinder; the pumping system combination is used for realizing reciprocating motion of the pumping main oil cylinder and providing a reversing signal for the oscillating oil cylinder reversing valve set; the reversing buffering valve set is used for reducing reversing impact of the pumping main oil cylinder. The invention further relates to a control method of the hydraulic control system and a pump containing the hydraulic control system. According to the hydraulic control system, when a pumping system is reversed, the displacement of the hydraulic pump does not need to be adjusted and part flow of the system is overflowed at the moment of reversing, so that the flow of the system is reduced, the movement speed of the pumping main oil cylinder is reduced and the system impact is reduced, and furthermore, the stable reversing of the pumping system is realized; the working efficiency of the system is improved and the fault rate is reduced.
Description
Technical Field
The invention relates to the field of hydraulic control, in particular to a hydraulic control system, a hydraulic control method and a pump.
Background
In a hydraulically driven double-piston type pumping system, when a main oil cylinder reaches a reversing position to perform reversing, in order to reduce impact on a cylinder barrel caused by rapid movement of a piston in the main oil cylinder, a variable pump is generally adopted as a pressure oil source in the related prior art, and when the main oil cylinder reaches the tail end position of the oil cylinder, the output flow of the variable pump is reduced to reduce the movement speed of the piston, so that the purpose of stable reversing is achieved.
However, the master cylinder in the pumping system has a very fast reversing frequency, and the output flow of the variable displacement pump needs to be frequently adjusted in order to reduce the reversing impact of the master cylinder, so that the service life of the variable displacement pump is shortened, and the working efficiency of the system is reduced. In addition, electrical elements such as proximity switches are used, so that the failure rate is high.
Disclosure of Invention
The invention aims to provide a hydraulic control system, a hydraulic control method and a hydraulic pump, which are used for reducing the movement speed of a piston by reducing the output flow of a variable pump when a pumping main oil cylinder reaches a reversing position, so that the aim of stably reversing is fulfilled, the system efficiency is improved, and the failure rate is reduced.
The present invention provides a hydraulic control system, including:
a swing cylinder (1);
a first pressure oil source (P1);
a pumping master cylinder (3.3, 3.4);
the swing oil cylinder reversing valve group (3.1) is used for reversing a piston of the swing oil cylinder (1);
the pumping system combination (3) is used for realizing the reciprocating motion of the pumping main oil cylinders (3.3, 3.4) and providing reversing signals for the reversing valve group (3.1) of the swing oil cylinder;
the reversing buffer valve group (2) is used for reducing reversing impact of the pumping main oil cylinders (3.3, 3.4);
wherein,
an oil supply passage (P11) and a control passage (P22) branched from the first pressure oil source (P1);
the first pressure oil source (P1) passes through the swing oil cylinder reversing valve group (3.1) through the oil supply oil way (P11) and then is connected with the swing oil cylinder (1) so as to supply oil to the swing oil cylinder (1) and promote the piston to reciprocate; the oil supply oil path (P11) is further branched into branch oil paths (4.1, 4.2) connected with the pumping system combination (3) at a position between the swing oil cylinder reversing valve group (3.1) and the swing oil cylinder (1), and the branch oil paths (4.1, 4.2) send hydraulic oil to the pumping system combination (3) so as to trigger the switching of the pumping system combination (3) between a first working state and a second working state of the pumping main oil cylinders (3.3, 3.4); in a first working state, the pumping system combination (3) limits the piston of the swing oil cylinder (1) to move towards a first direction; in a second working state, the pumping system combination (3) limits the piston of the swing oil cylinder (1) to move towards a second direction;
a control oil path (P22) of the first pressure oil source (P1) passes through the pumping system assembly (3) and then is connected with the swing oil cylinder reversing valve group (3.1) so as to convey control oil to the swing oil cylinder reversing valve group (3.1), and the swing oil cylinder reversing valve group (3.1) can change the moving direction of a piston of the swing oil cylinder (1) after being triggered by hydraulic oil; and a control oil path (P22) of the first pressure oil source (P1) passes through the pumping system combination (3) and then is connected with the reversing buffer valve group (2) so as to overflow part of hydraulic oil flowing to the pumping main oil cylinders (3.3 and 3.4) through the reversing buffer valve group (2).
Further, the pumping system combination (3) further comprises:
the oil pump comprises a reversing valve group (3.1), a comparison valve group (3.2) and a second pressure oil source (P2);
the pumping main oil cylinders (3.3, 3.4) comprise a first pumping oil cylinder (3.3) and a second pumping oil cylinder (3.4);
the second pressure oil source (P2) is communicated with an oil inlet of the reversing valve group (3.1) through an oil supply oil way (P11), two working oil ports of the reversing valve group (3.1) are respectively connected with a rodless cavity of the first pumping oil cylinder (3.3) and a rodless cavity of the second pumping oil cylinder (3.4), and a rod cavity of the first pumping oil cylinder (3.3) and a rod cavity of the second pumping oil cylinder (3.4) are mutually connected; the branch oil paths (4.1, 4.2) are connected with the left control end and the right control end of the reversing valve group (3.1) to control the reversing valve group (3.1) to enable the second pressure oil source (P2) to selectively supply oil to the rodless cavity of the first pumping oil cylinder (3.3) or the rodless cavity of the second pumping oil cylinder (3.4); the reversing valve group (3.1) is also connected with the reversing buffer valve group (2) and is used for draining hydraulic oil in a rodless cavity of the first pumping oil cylinder (3.3) or the second pumping oil cylinder (3.4);
the comparison valve group (3.2) is respectively connected with a rod cavity of the first pumping oil cylinder (3.3) and a rod cavity of the second pumping oil cylinder (3.4) so as to convey one part of hydraulic oil of a control oil way (P22) of the first pressure oil source (P1) to a first position or a second position of the swing oil cylinder reversing valve group (3.1) and convey the other part of hydraulic oil to the reversing buffer valve group (2) according to a first hydraulic oil signal of the rod cavity of the first pumping oil cylinder (3.3) or a second hydraulic oil signal of the rod cavity of the second pumping oil cylinder (3.4) to control the reversing buffer valve group (2) to overflow.
Further, the rod cavity of the first pumping cylinder (3.3) comprises a first trigger mechanism (S1), and when the piston of the first pumping cylinder (3.3) approaches the bottom of the rod cavity by a preset distance, the rod cavity of the first pumping cylinder (3.3) sends the first hydraulic oil signal to the comparison valve group (3.2); and the rod cavity of the second pumping oil cylinder (3.4) comprises a second trigger mechanism (S2), and when the piston of the second pumping oil cylinder (3.4) is close to the bottom of the rod cavity for a preset distance, the rod cavity of the second pumping oil cylinder (3.4) sends the second hydraulic oil signal to the comparison valve group (3.2).
Further, the first triggering mechanism (S1) comprises a first outlet (a) and a second outlet (b) arranged on the cylinder wall of the first pumping cylinder (3.3) at a preset distance from the bottom of the rod cavity, the distance between the first and second outlets being greater than the thickness of the piston, the first outlet (a) and the second outlet (b) being respectively connected to the comparison valve group (3.2); the second trigger mechanism (S2) comprises a third outlet (c) and a fourth outlet (d) which are arranged on the wall of the second pumping oil cylinder (3.4) at a preset distance from the bottom of the rod cavity, the distance between the third outlet and the fourth outlet is larger than the thickness of the piston, and the third outlet (c) and the fourth outlet (d) are respectively connected to the comparison valve group (3.2).
Further, the comparison valve group (3.2) comprises a first comparison valve (3.2.1) and a second comparison valve (3.2.2), the left end and the right end of the first comparison valve (3.2.1) are respectively connected with the first outlet (a) and the second outlet (b), the left end and the right end of the second comparison valve (3.2.2) are respectively connected with the third outlet (c) and the fourth outlet (d), the control oil path (P22) comprises a first control oil path and a second control oil path which are connected in parallel, the first control oil path is divided into a first oil path and a second oil path after passing through the first comparison valve (3.2.1), the first oil path is connected with the swing oil cylinder reversing valve group (3.1), and the second oil path is connected with the reversing buffer valve group (2) through a first one-way valve (V1); the second control oil way is divided into a third oil way and a fourth oil way after passing through the second comparison valve (3.2.2), the third oil way is connected with the swing oil cylinder reversing valve group (3.1), and the fourth oil way is connected with the reversing buffer valve group (2) through a second one-way valve (V2).
Further, the reversing buffer valve group (2) further comprises: the hydraulic control system comprises a first overflow valve (O1), a second overflow valve (O2) and a hydraulic control reversing valve (S), wherein the first overflow valve (O1) is connected with the hydraulic control reversing valve (S) through a control oil path (P22) of the first overflow valve, and the hydraulic control reversing valve (S) is connected with the second overflow valve (O2); the second pressure oil source (P2) is connected with the first overflow valve (O1) and overflows the hydraulic oil in the rodless cavity of the first pumping oil cylinder (3.3) or the second pumping oil cylinder (3.4) through the first overflow valve (O1); and a second oil way of the first control oil way and a fourth oil way of the second control oil way are connected in parallel and then are connected with the hydraulic control reversing valve (S) so as to control the reversing buffer valve group (2) to overflow.
The invention also provides a control method of the hydraulic control system, which comprises the following steps:
in a first working state of the pumping main oil cylinders (3.3, 3.4), hydraulic oil in an oil supply oil path (P11) of the first pressure oil source (P1) acts on the swing oil cylinder (1), so that a piston of the swing oil cylinder (1) moves along a first direction;
when the piston moves to a first preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing oil cylinder reversing valve group (3.1) to trigger the swing oil cylinder reversing valve group (3.1) to reverse the piston, and the other part of the control oil in the control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2) to overflow part of hydraulic oil flowing to the pumping main cylinders (3.3, 3.4) through the reversing buffer valve group (2) to reduce system flow, wherein the movement speed of the piston of the pumping main cylinders (3.3, 3.4) is reduced; meanwhile, part of hydraulic oil in an oil supply oil path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) through the branch oil path (4.1, 4.2) to trigger a second working state of the pumping main oil cylinder (3.3, 3.4); in a second working state of the pumping main oil cylinders (3.3, 3.4), hydraulic oil in an oil supply oil path (P11) of the second pressure oil source (P2) acts on the swing oil cylinder (1), so that a piston of the swing oil cylinder (1) moves along a second direction;
when the piston moves to a second preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing cylinder reversing valve group (3.1) to trigger the piston reversing, and the other part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2) to overflow part of hydraulic oil flowing to the pumping main cylinders (3.3, 3.4) through the reversing buffer valve group (2) to reduce the system flow, wherein the piston movement speed of the pumping main cylinders (3.3, 3.4) is reduced, and simultaneously, part of hydraulic oil in an oil supply path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) through the branch oil paths (4.1, 4.2) to trigger the pumping main cylinder (3.3, 3.4) returning to the first working state.
Further, in a first operating state of the pumping master cylinder (3.3, 3.4), hydraulic oil in an oil supply oil passage (P11) of the first pressure oil source (P1) is supplied to the swing cylinder (1), moving a piston of the swing cylinder (1) in a first direction;
when the piston moves to a first preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing cylinder reversing valve group (3.1) to trigger the piston reversing, the other part of the control oil in the control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2), part of hydraulic oil flowing to the pumping main cylinders (3.3, 3.4) overflows through the reversing buffer valve group (2) to reduce the system flow, the piston movement speed of the pumping main cylinders (3.3, 3.4) is reduced, and part of the hydraulic oil in the oil supply path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) to trigger a second working state of the pumping main cylinders (3.3, 3.4); in a second working state of the pumping master cylinders (3.3, 3.4), supplying hydraulic oil in an oil supply oil path (P11) of the second pressure oil source (P2) to the swing cylinder (1) to move a piston of the swing cylinder (1) in a second direction;
when the piston moves to a second preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing oil cylinder reversing valve group (3.1) to trigger the reversing of the piston, the other part of the control oil in the control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2), part of hydraulic oil flowing to the pumping main oil cylinders (3.3, 3.4) overflows through the reversing buffer valve group (2) to reduce the system flow, the piston movement speed of the main cylinders is reduced at the moment, and part of the hydraulic oil in an oil supply path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) to trigger the pumping main cylinders (3.3, 3.4) to return to the first working state.
Further, comprising: a second pressure oil source (P2) triggers a first position of the reversing valve group (3.1) to convey hydraulic oil of the second pressure oil source (P2) to a rodless cavity of the first pumping oil cylinder (3.3) through the first branch, a piston of the first pumping oil cylinder (3.3) moves, when the piston moves to a first preset position away from the bottom of the rod cavity, the first pumping oil cylinder (3.3) sends a first hydraulic oil signal to the comparison valve group (3.2), the comparison valve group (3.2) is opened to convey a part of hydraulic oil of a control oil path (P22) of the first pressure oil source (P1) to the swing oil cylinder reversing valve group (3.1), and the swing oil cylinder reversing valve group (3.1) reverses the piston of the swing oil cylinder (1); meanwhile, the other part of hydraulic oil is conveyed to the reversing buffer valve group (2) to overflow;
a second pressure oil source (P2) triggers a second position of the reversing valve group (3.1) to convey hydraulic oil of the second pressure oil source (P2) to a rodless cavity of the second pumping cylinder (3.4) through the second branch, a piston of the second pumping cylinder (3.4) moves, when the piston moves to a second preset position away from the bottom of the rod cavity, the second pumping cylinder (3.4) sends a second hydraulic oil signal to the comparison valve group (3.2), the comparison valve group (3.2) is opened to convey a part of hydraulic oil of a control oil path (P22) of the second pressure oil source (P2) to the swing cylinder reversing valve group (3.1), and the swing cylinder reversing valve group (3.1) reverses the piston of the swing cylinder (1); meanwhile, the other part of hydraulic oil is conveyed to the reversing buffer valve group (2) to overflow.
Further, the first preset distance is located between the first outlet (a) and the second outlet (b), and the distance between the first outlet and the second outlet is larger than the thickness of the piston;
the second predetermined distance is located between the third and fourth outlets, and the distance between the third and fourth outlets is greater than the thickness of the piston.
Further, when a piston of the first pumping oil cylinder (3.3) is located between the first outlet (a) and the second outlet (b), the first comparison valve (3.2.1) is triggered, hydraulic oil of the first oil path triggers the swing oil cylinder reversing valve set (3.1) to reverse the swing oil cylinder (1), and the second oil path triggers the reversing buffer valve set (2) to overflow;
when the piston of the second pumping oil cylinder (3.4) is located between the third outlet (c) and the fourth outlet (d), the second comparison valve (3.2.2) is triggered, hydraulic oil of the third oil way triggers the swing oil cylinder reversing valve set (3.1) to reverse the swing oil cylinder (1), and hydraulic oil of the fourth oil way triggers the reversing buffer valve set (2) to overflow.
The invention also provides a pump which comprises the hydraulic control system.
According to the hydraulic control system, the control method and the pump, when the pumping system is reversed, the displacement of the hydraulic pump is not required to be adjusted, but partial flow of the system overflows at the moment of reversing, so that the flow of the system is reduced, the movement speed of the piston of the pumping main oil cylinder is reduced to reduce the system impact, the stable reversing of the pumping system is realized, the working efficiency of the system is improved, and the failure rate is reduced.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:
FIG. 1 is a schematic diagram of one embodiment of a hydraulic control system of the present invention.
Detailed Description
The technical solution of the present invention is further described in detail by the accompanying drawings and embodiments.
Referring to fig. 1, a hydraulic control system according to an embodiment of the present invention includes:
a swing oil cylinder 1;
a first pressure source P1;
pumping the main oil cylinder 3.3, 3.4;
the swing oil cylinder reversing valve group 3.1 is used for reversing a piston of the swing oil cylinder 1;
the pumping system combination 3 is used for realizing reciprocating motion of the pumping main oil cylinders 3.3 and 3.4 and providing reversing signals for the reversing valve group 3.1 of the swing oil cylinder;
the reversing buffer valve group 2 is used for reducing reversing impact of the pumping main oil cylinders 3.3 and 3.4;
wherein,
an oil supply passage P11 and a control passage P22 branch off from the first pressure oil source P1;
the first pressure oil source P1 passes through the swing oil cylinder reversing valve group 3.1 through the oil supply oil path P11 and then is connected with the swing oil cylinder 1 so as to supply oil to the swing oil cylinder 1 and promote the piston to reciprocate; the oil supply oil path P11 further branches into branch oil paths 4.1 and 4.2 connected to the pumping system assembly 3 at a position between the swing oil cylinder reversing valve group 3.1 and the swing oil cylinder 1, and the branch oil paths 4.1 and 4.2 send hydraulic oil to the pumping system assembly 3 to trigger the switching of the pumping system assembly 3 between the first working state and the second working state of the pumping main cylinders 3.3 and 3.4; in a first working state, the pumping system combination 3 limits the piston of the swing oil cylinder 1 to move towards a first direction; in a second working state, the pumping system combination 3 limits the piston of the swing oil cylinder 1 to move towards a second direction;
a control oil path P22 of the first pressure oil source P1 passes through the pumping system assembly 3 and then is connected with the swing oil cylinder reversing valve group 3.1 to convey control oil to the swing oil cylinder reversing valve group 3.1, and the swing oil cylinder reversing valve group 3.1 can change the moving direction of a piston of the swing oil cylinder 1 after being triggered by hydraulic oil; and a control oil path P22 of the first pressure oil source P1 is connected with the reversing buffer valve group 2 after passing through the pumping system assembly 3, so that part of hydraulic oil flowing to the pumping main oil cylinders 3.3 and 3.4 overflows through the reversing buffer valve group 2.
Due to the existence of the energy accumulator 6, the swing oil cylinder and the reversing valve group 3.1 quickly complete reversing, the swing oil cylinder and the pumping main oil cylinder almost start reversing at the same time, the swing oil cylinder can be reversed in place within a short time of about 0.2S, and the reversed pumping main oil cylinder moves forwards or backwards.
The embodiment further comprises a reversing valve group 3.1, a comparison valve group 3.2 and a second pressure oil source P2;
the pumping main oil cylinders 3.3 and 3.4 comprise a first pumping oil cylinder 3.3 and a second pumping oil cylinder 3.4;
the second pressure oil source P2 is communicated with an oil inlet of the reversing valve group 3.1 through an oil supply path P11, two working oil ports of the reversing valve group 3.1 are respectively connected with a rodless cavity of the first pumping oil cylinder 3.3 and a rodless cavity of the second pumping oil cylinder 3.4, and a rod cavity of the first pumping oil cylinder 3.3 and a rod cavity of the second pumping oil cylinder 3.4 are connected with each other; the branch oil paths 4.1 and 4.2 are connected with the left control end and the right control end of the reversing valve group 3.1 to control the reversing valve group 3.1 to enable the second pressure oil source P2 to selectively supply oil to the rodless cavity of the first pumping oil cylinder 3.3 or the rodless cavity of the second pumping oil cylinder 3.4; the reversing valve group 3.1 is also connected with the reversing buffer valve group 2 to drain hydraulic oil in a rodless cavity of the first pumping oil cylinder 3.3 or the second pumping oil cylinder 3.4;
the comparison valve group 3.2 is respectively connected with a rod cavity of the first pumping oil cylinder 3.3 and a rod cavity of the second pumping oil cylinder 3.4, so that one part of hydraulic oil of a control oil path P22 of the first pressure oil source P1 is conveyed to a first position or a second position of the swing oil cylinder reversing valve group 3.1, and the other part of hydraulic oil is conveyed to the reversing buffer valve group 2 to control the reversing buffer valve group 2 to overflow according to a first hydraulic oil signal of the rod cavity of the first pumping oil cylinder 3.3 or a second hydraulic oil signal of the rod cavity of the second pumping oil cylinder 3.4.
The rod cavity of the first pumping cylinder 3.3 comprises a first trigger mechanism S1, and when the piston of the first pumping cylinder 3.3 approaches the bottom of the rod cavity by a preset distance, the rod cavity of the first pumping cylinder 3.3 sends the first hydraulic oil signal to the comparison valve group 3.2; the rod cavity of the second pumping cylinder 3.4 comprises a second trigger mechanism S2, and when the piston of the second pumping cylinder 3.4 approaches the bottom of the rod cavity for a preset distance, the rod cavity of the second pumping cylinder 3.4 sends the second hydraulic oil signal to the comparison valve group 3.2.
The first trigger mechanism S1 includes a first outlet a and a second outlet b arranged on the cylinder wall of the first pumping cylinder 3.3 at a preset distance from the bottom of the rod chamber, the distance between the first and second outlets is greater than the thickness of the piston, and the first outlet a and the second outlet b are respectively connected to the comparison valve group 3.2; the second trigger mechanism S2 includes a third outlet c and a fourth outlet d that are disposed on the cylinder wall of the second pumping cylinder 3.4 at a preset distance from the bottom of the rod cavity, the distance between the third and fourth outlets is greater than the thickness of the piston, and the third outlet c and the fourth outlet d are connected to the comparison valve group 3.2, respectively.
The comparison valve group 3.2 comprises a first comparison valve 3.2.1 and a second comparison valve 3.2.2, the left end and the right end of the first comparison valve 3.2.1 are respectively connected with the first outlet a and the second outlet b, the left end and the right end of the second comparison valve 3.2.2 are respectively connected with the third outlet c and the fourth outlet d, the control oil path P22 comprises a first control oil path and a second control oil path which are connected in parallel, the first control oil path is divided into a first oil path and a second oil path after passing through the first comparison valve 3.2.1, the first oil path is connected with the swing oil cylinder reversing valve group 3.1, and the second oil path is connected with the reversing buffer valve group 2 through a first one-way valve V1; the second control oil path is divided into a third oil path and a fourth oil path after passing through the second comparison valve 3.2.2, the third oil path is connected with the swing oil cylinder reversing valve group 3.1, and the fourth oil path is connected with the reversing buffer valve group 2 through a second one-way valve V2.
The reversing buffer valve group 2 further comprises: the hydraulic control system comprises a first overflow valve O1, a second overflow valve O2 and a hydraulic control reversing valve S, wherein the first overflow valve O1 is connected with the hydraulic control reversing valve S through a control oil path P22 of the first overflow valve O2, and the hydraulic control reversing valve S is connected with the second overflow valve O2; the second pressure oil source P2 is connected to the first overflow valve O1, and overflows hydraulic oil in the rodless chamber of the first pumping cylinder 3.3 or the second pumping cylinder 3.4 through the first overflow valve O1; and a second oil way of the first control oil way and a fourth oil way of the second control oil way are connected in parallel and then are connected with the hydraulic control reversing valve S to control the reversing buffer valve group 2 to overflow.
Meanwhile, the invention also provides a control method of the hydraulic control system, which comprises the following steps: in a first working state of the pumping master cylinders 3.3 and 3.4, the hydraulic oil in the oil supply path P11 of the first pressure oil source P1 is applied to the swing cylinder 1, so that the piston of the swing cylinder 1 moves in a first direction;
when the piston moves to a first preset reversing position, one part of control oil in a control oil path P22 of the first pressure oil source P1 is conveyed to the swing oil cylinder reversing valve group 3.1 to trigger the swing oil cylinder reversing valve group 3.1 to reverse the piston, and the other part of control oil in a control oil path P22 of the first pressure oil source P1 is conveyed to the reversing buffer valve group 2 to overflow part of hydraulic oil flowing to the pumping main cylinders 3.3 and 3.4 through the reversing buffer valve group 2 to reduce the system flow, wherein the piston movement speed of the pumping main cylinders 3.3 and 3.4 main oil pumps is reduced; meanwhile, part of hydraulic oil in the oil supply oil path P11 of the first pressure oil source P1 is conveyed to the pumping system combination 3 through the branch oil paths 4.1 and 4.2 so as to trigger the second working state of the pumping main oil cylinders 3.3 and 3.4; in a second working state of the pumping master cylinders 3.3 and 3.4, the hydraulic oil in the oil supply path P11 of the second pressure oil source P2 is applied to the swing cylinder 1, so that the piston of the swing cylinder 1 moves in a second direction;
when the piston moves to a second preset reversing position, one part of the control oil in the control oil path P22 of the first pressure oil source P1 is conveyed to the swing cylinder reversing valve group 3.1 to trigger the piston reversing, and the other part of the control oil in the control oil path P22 of the first pressure oil source P1 is conveyed to the reversing buffer valve group 2 to overflow part of the hydraulic oil flowing to the pumping main cylinders 3.3 and 3.4 through the reversing buffer valve group 2 to reduce the system flow, at which time the piston movement speed of the pumping main cylinders 3.3 and 3.4 is reduced, and at the same time, part of the hydraulic oil in the oil supply path P11 of the first pressure oil source P1 is conveyed to the pumping system combination 3 through the branch oil paths 4.1 and 4.2 to trigger the pumping main cylinders 3.3 and 3.4 to return to the first working state.
In a first operating state of the pumping master cylinders 3.3, 3.4, the hydraulic oil in the oil supply path P11 of the first pressure oil source P1 is supplied to the swing cylinder 1, so that the piston of the swing cylinder 1 moves in a first direction;
when the piston moves to a first preset reversing position, one part of the control oil in the control oil path P22 of the first pressure oil source P1 is conveyed to the swing cylinder reversing valve group 3.1 to trigger the piston reversing, the other part of the control oil in the control oil path P22 of the first pressure oil source P1 is conveyed to the reversing buffer valve group 2, part of the hydraulic oil flowing to the pumping main cylinders 3.3 and 3.4 overflows through the reversing buffer valve group 2 to reduce the system flow, the piston movement speed of the pumping main cylinders 3.3 and 3.4 is reduced at the moment, and part of the hydraulic oil in the oil supply path P11 of the first pressure oil source P1 is conveyed to the pumping system combination 3 to trigger a second working state of the pumping main cylinders 3.3 and 3.4; in a second operating state of the pumping master cylinders 3.3, 3.4, the hydraulic oil in the oil supply path P11 of the second pressure oil source P2 is supplied to the swing cylinder 1, so that the piston of the swing cylinder 1 moves in a second direction;
when the piston moves to a second preset reversing position, one part of the control oil in the control oil path P22 of the first pressure oil source P1 is conveyed to the swing cylinder reversing valve group 3.1 to trigger the reversing of the piston, the other part of the control oil in the control oil path P22 of the first pressure oil source P1 is conveyed to the reversing buffer valve group 2, part of the hydraulic oil flowing to the pumping main cylinders 3.3 and 3.4 overflows through the reversing buffer valve group 2 to reduce the system flow, the piston movement speed of the main oil pump is reduced, and part of the hydraulic oil in the oil supply oil path P11 of the first pressure oil source P1 is conveyed to the pumping system combination 3 to trigger the pumping main cylinders 3.3 and 3.4 to return to the first working state.
The method comprises the following steps: a second pressure oil source P2 triggers a first position of the reversing valve group 3.1 to convey hydraulic oil of the second pressure oil source P2 to a rodless cavity of the first pumping oil cylinder 3.3 through the first branch, a piston of the first pumping oil cylinder 3.3 moves, when the piston moves to a first preset position away from the bottom of a rod cavity, the first pumping oil cylinder 3.3 sends a first hydraulic oil signal to the comparison valve group 3.2, the comparison valve group 3.2 is opened to convey a part of hydraulic oil of a control oil path P22 of the first pressure oil source P1 to the swing oil cylinder reversing valve group 3.1, and the swing oil cylinder reversing valve group 3.1 reverses the piston of the swing oil cylinder 1; meanwhile, the other part of hydraulic oil is conveyed to the reversing buffer valve group 2 to overflow;
a second pressure oil source P2 triggers a second position of the reversing valve group 3.1 to convey hydraulic oil of the second pressure oil source P2 to a rodless cavity of the second pumping cylinder 3.4 through the second branch, a piston of the second pumping cylinder 3.4 moves, when the piston moves to a second preset position away from the bottom of the rod cavity, the second pumping cylinder 3.4 sends a second hydraulic oil signal to the comparison valve group 3.2, the comparison valve group 3.2 is opened to convey a part of hydraulic oil of a control oil path P22 of the second pressure oil source P2 to the swing cylinder reversing valve group 3.1, and the swing cylinder reversing valve group 3.1 reverses the piston of the swing cylinder 1; meanwhile, the other part of the hydraulic oil is conveyed to the reversing buffer valve group 2 to overflow.
The first preset distance is positioned between a first outlet a and a second outlet b, and the distance between the first outlet and the second outlet is greater than the thickness of the piston;
the second predetermined distance is located between the third and fourth outlets, and the distance between the third and fourth outlets is greater than the thickness of the piston.
When the piston of the first pumping oil cylinder 3.3 is located between the first outlet a and the second outlet b, the first comparison valve 3.2.1 is triggered, hydraulic oil of the first oil path triggers the swing oil cylinder reversing valve group 3.1 to reverse the swing oil cylinder 1, and the second oil path triggers the reversing buffer valve group 2 to overflow;
when the piston of the second pumping oil cylinder 3.4 is located between the third outlet c and the fourth outlet d, the second comparison valve 3.2.2 is triggered, hydraulic oil of the third oil path triggers the swing oil cylinder reversing valve group 3.1 to reverse the swing oil cylinder 1, and hydraulic oil of the fourth oil path triggers the reversing buffer valve group 2 to overflow.
The working process of this embodiment is further explained below with reference to the structural features of this embodiment: assuming that the reversing valve group 3.1 is at the right position at the initial position, the second pressure source P2 enters the rodless cavity of the first pumping cylinder 3.3 through the reversing valve group 3.1 to push the piston to move forward, and the piston of the second pumping cylinder 3.4 moves backward, when the piston of the first pumping cylinder 3.3 moves to the front end of the cylinder, and passes through the port a, because the pressure of the port a is greater than the pressure of the port b (the port b is located at the bottom of the cylinder, and the distance between the port a and the piston when moving to the bottom is generally 20-50mm), the port a sends out signal oil to push the comparison valve 3.2.1 to work at the right position, the P2 pushes the reversing valve in the reversing valve group 4 of the swing cylinder to work at the left position through the comparison valve 3.2.1, and pushes the comparison valve 3.1 to work at the right position through the first check valve V1 at the. At this time, the control oil of the O1 (the valve core of the second pumping cylinder 3.4 is provided with an orifice, and part of the hydraulic oil of the second pressure source P2 is used as the control oil for controlling the opening and closing of the valve core of the second pumping cylinder 3.4) overflows through the S and the O2, (the set pressure of the O2 is low, generally about 0.4 MPa), the main valve core of the O1 opens the P2 overflow, the system flow is reduced, and the movement speed of the piston of the pumping main cylinder is reduced. P2 is divided into two paths after passing through a reversing valve in a reversing valve group 4 of a swing oil cylinder, one path enters a first swing oil cylinder 1.1 to enable the swing oil cylinder to be reversed, the other path pushes the reversing valve group 3.1 to work at the left position, a second pressure source P2 enters a rodless cavity of a second pumping oil cylinder 3.4 through 3.1 to push a piston to move forwards, the piston of the first pumping oil cylinder 3.3 moves backwards to achieve reversing of a main oil cylinder, when the piston of the second pumping oil cylinder 3.4 moves to the front end of the oil cylinder and passes through a port c, the pressure of the port c is larger than that of the port d, the port c sends signal oil to push a second comparison valve 3.2.2 to work at the right position, P2 pushes the reversing valve in the reversing valve group 4 of the swing oil cylinder to work at the right position through the second comparison valve 3.2.2, and the other path of the second comparison valve 3.2.2 through a second one-way valve V2. When the control oil of the O1 overflows through the S and the O2, the main valve core of the O1 opens the P2 to overflow, the flow rate of the system is reduced, and the movement speed of a piston pumping the main oil cylinder is reduced. One path of the P2 enters the second swing oil cylinder 1.2 to change the direction of the swing cylinder, the other path of the P2 pushes the reversing valve group 3.1 to work at the right position, the second pressure source P2 enters the rodless cavity of the first pumping oil cylinder 3.3 through the reversing valve group 3.1 to push the piston to move forwards, and the piston of the first pumping oil cylinder 3.3 moves backwards to realize the reversing of the main oil cylinder, thereby sequentially realizing the reciprocating motion of the oil cylinders.
The invention also provides a pump which comprises the hydraulic control system.
According to the hydraulic control system, the control method and the pump, when the pumping system is reversed, the displacement of the hydraulic pump is not required to be adjusted, but partial flow of the system overflows at the moment of reversing, so that the flow of the system is reduced, the movement speed of the pumping main oil cylinder is reduced to reduce the system impact, the stable reversing of the pumping system is realized, the working efficiency of the system is improved, and the failure rate is reduced.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention and not to limit it; although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art will understand that: modifications to the specific embodiments of the invention or equivalent substitutions for parts of the technical features may be made; without departing from the spirit of the present invention, it is intended to cover all aspects of the invention as defined by the appended claims.
Claims (12)
1. A hydraulic control system, comprising:
a swing cylinder (1);
a first pressure oil source (P1);
a pumping master cylinder (3.3, 3.4);
the swing oil cylinder reversing valve group (3.1) is used for reversing a piston of the swing oil cylinder (1);
the pumping system combination (3) is used for realizing the reciprocating motion of the pumping main oil cylinders (3.3, 3.4) and providing reversing signals for the reversing valve group (3.1) of the swing oil cylinder;
the reversing buffer valve group (2) is used for reducing reversing impact of the pumping main oil cylinders (3.3, 3.4);
wherein,
an oil supply passage (P11) and a control passage (P22) branched from the first pressure oil source (P1);
the first pressure oil source (P1) passes through the swing oil cylinder reversing valve group (3.1) through the oil supply oil way (P11) and then is connected with the swing oil cylinder (1) so as to supply oil to the swing oil cylinder (1) and promote the piston to reciprocate; the oil supply oil path (P11) is further branched into branch oil paths (4.1, 4.2) connected with the pumping system combination (3) at a position between the swing oil cylinder reversing valve group (3.1) and the swing oil cylinder (1), and the branch oil paths (4.1, 4.2) send hydraulic oil to the pumping system combination (3) so as to trigger the switching of the pumping system combination (3) between a first working state and a second working state of the pumping main oil cylinders (3.3, 3.4); in a first working state, the pumping system combination (3) limits the piston of the swing oil cylinder (1) to move towards a first direction; in a second working state, the pumping system combination (3) limits the piston of the swing oil cylinder (1) to move towards a second direction;
a control oil path (P22) of the first pressure oil source (P1) passes through the pumping system assembly (3) and then is connected with the swing oil cylinder reversing valve group (3.1) so as to convey control oil to the swing oil cylinder reversing valve group (3.1), and the swing oil cylinder reversing valve group (3.1) can change the moving direction of a piston of the swing oil cylinder (1) after being triggered by hydraulic oil; and a control oil path (P22) of the first pressure oil source (P1) passes through the pumping system combination (3) and then is connected with the reversing buffer valve group (2) so as to overflow part of hydraulic oil flowing to the pumping main oil cylinders (3.3 and 3.4) through the reversing buffer valve group (2).
2. The hydraulic control system of claim 1, wherein the pumping system combination (3) further comprises:
the oil pump comprises a reversing valve group (3.1), a comparison valve group (3.2) and a second pressure oil source (P2);
the pumping main oil cylinders (3.3, 3.4) comprise a first pumping oil cylinder (3.3) and a second pumping oil cylinder (3.4);
the second pressure oil source (P2) is communicated with an oil inlet of the reversing valve group (3.1) through an oil supply oil way (P11), two working oil ports of the reversing valve group (3.1) are respectively connected with a rodless cavity of the first pumping oil cylinder (3.3) and a rodless cavity of the second pumping oil cylinder (3.4), and a rod cavity of the first pumping oil cylinder (3.3) and a rod cavity of the second pumping oil cylinder (3.4) are mutually connected; the branch oil paths (4.1, 4.2) are connected with the left control end and the right control end of the reversing valve group (3.1) to control the reversing valve group (3.1) to enable the second pressure oil source (P2) to selectively supply oil to the rodless cavity of the first pumping oil cylinder (3.3) or the rodless cavity of the second pumping oil cylinder (3.4); the reversing valve group (3.1) is also connected with the reversing buffer valve group (2) and is used for draining hydraulic oil in a rodless cavity of the first pumping oil cylinder (3.3) or the second pumping oil cylinder (3.4);
the comparison valve group (3.2) is respectively connected with a rod cavity of the first pumping oil cylinder (3.3) and a rod cavity of the second pumping oil cylinder (3.4) so as to convey one part of hydraulic oil of a control oil way (P22) of the first pressure oil source (P1) to a first position or a second position of the swing oil cylinder reversing valve group (3.1) and convey the other part of hydraulic oil to the reversing buffer valve group (2) according to a first hydraulic oil signal of the rod cavity of the first pumping oil cylinder (3.3) or a second hydraulic oil signal of the rod cavity of the second pumping oil cylinder (3.4) to control the reversing buffer valve group (2) to overflow.
3. The hydraulic control system according to claim 2, characterized in that the rod chamber of the first pumping cylinder (3.3) comprises a first triggering mechanism (S1), the rod chamber of the first pumping cylinder (3.3) sending the first hydraulic oil signal to the comparison valve group (3.2) when the piston of the first pumping cylinder (3.3) approaches the bottom of the rod chamber by a preset distance; and the rod cavity of the second pumping oil cylinder (3.4) comprises a second trigger mechanism (S2), and when the piston of the second pumping oil cylinder (3.4) is close to the bottom of the rod cavity for a preset distance, the rod cavity of the second pumping oil cylinder (3.4) sends the second hydraulic oil signal to the comparison valve group (3.2).
4. The hydraulic control system according to claim 3, characterized in that the first triggering mechanism (S1) comprises a first outlet (a) and a second outlet (b) arranged on the cylinder wall of the first pumping cylinder (3.3) at a preset distance from the bottom of the rod chamber, the distance between the first and second outlets being greater than the thickness of the piston, the first outlet (a) and second outlet (b) being connected to the group of comparison valves (3.2), respectively; the second trigger mechanism (S2) comprises a third outlet (c) and a fourth outlet (d) which are arranged on the wall of the second pumping oil cylinder (3.4) at a preset distance from the bottom of the rod cavity, the distance between the third outlet and the fourth outlet is larger than the thickness of the piston, and the third outlet (c) and the fourth outlet (d) are respectively connected to the comparison valve group (3.2).
5. The hydraulic control system according to claim 4, characterized in that the comparison valve group (3.2) comprises a first comparison valve (3.2.1) and a second comparison valve (3.2.2), the left and right ends of the first comparison valve (3.2.1) are respectively connected with the first outlet (a) and the second outlet (b), the left and right ends of the second comparison valve (3.2.2) are respectively connected with the third outlet (c) and the fourth outlet (d), the control oil path (P22) comprises a first control oil path and a second control oil path which are connected in parallel, the first control oil path is divided into a first oil path and a second oil path after passing through the first comparison valve (3.2.1), the first oil path is connected with the swing cylinder reversing valve group (3.1), and the second oil path is connected with the reversing buffer valve group (2) through a first check valve (V1); the second control oil way is divided into a third oil way and a fourth oil way after passing through the second comparison valve (3.2.2), the third oil way is connected with the swing oil cylinder reversing valve group (3.1), and the fourth oil way is connected with the reversing buffer valve group (2) through a second one-way valve (V2).
6. The hydraulic control system of claim 5, wherein the set of reversing cushion valves (2) further comprises: the hydraulic control system comprises a first overflow valve (O1), a second overflow valve (O2) and a hydraulic control reversing valve (S), wherein the first overflow valve (O1) is connected with the hydraulic control reversing valve (S) through a control oil path (P22) of the first overflow valve, and the hydraulic control reversing valve (S) is connected with the second overflow valve (O2); the second pressure oil source (P2) is connected with the first overflow valve (O1) and overflows the hydraulic oil in the rodless cavity of the first pumping oil cylinder (3.3) or the second pumping oil cylinder (3.4) through the first overflow valve (O1); and a second oil way of the first control oil way and a fourth oil way of the second control oil way are connected in parallel and then are connected with the hydraulic control reversing valve (S) so as to control the reversing buffer valve group (2) to overflow.
7. A control method of a hydraulic control system according to any one of claims 1 to 6, comprising:
in a first working state of the pumping main oil cylinders (3.3, 3.4), hydraulic oil in an oil supply oil path (P11) of the first pressure oil source (P1) acts on the swing oil cylinder (1), so that a piston of the swing oil cylinder (1) moves along a first direction;
when the piston moves to a first preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing oil cylinder reversing valve group (3.1) to trigger the swing oil cylinder reversing valve group (3.1) to reverse the piston, and the other part of the control oil in the control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2) to overflow part of hydraulic oil flowing to the pumping main oil cylinders (3.3, 3.4) through the reversing buffer valve group (2) to reduce system flow, and at the moment, the piston movement speed of the main oil pumps of the pumping main oil cylinders (3.3, 3.4) is reduced; meanwhile, part of hydraulic oil in an oil supply oil path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) through the branch oil path (4.1, 4.2) to trigger a second working state of the pumping main oil cylinder (3.3, 3.4); in a second working state of the pumping main oil cylinders (3.3, 3.4), hydraulic oil in an oil supply oil path (P11) of the second pressure oil source (P2) acts on the swing oil cylinder (1), so that a piston of the swing oil cylinder (1) moves along a second direction;
when the piston moves to a second preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing cylinder reversing valve group (3.1) to trigger the piston reversing, and the other part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2) to overflow part of hydraulic oil flowing to the pumping main cylinders (3.3, 3.4) through the reversing buffer valve group (2) to reduce the system flow, wherein the piston movement speed of the pumping main cylinders (3.3, 3.4) is reduced, and simultaneously, part of hydraulic oil in an oil supply path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) through the branch oil paths (4.1, 4.2) to trigger the pumping main cylinder (3.3, 3.4) returning to the first working state.
8. The method of claim 7,
in a first working state of the pumping master cylinders (3.3, 3.4), hydraulic oil in an oil supply oil path (P11) of the first pressure oil source (P1) is supplied to the swing cylinder (1), so that a piston of the swing cylinder (1) moves in a first direction;
when the piston moves to a first preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing cylinder reversing valve group (3.1) to trigger the piston reversing, the other part of the control oil in the control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2), part of hydraulic oil flowing to the pumping main cylinders (3.3, 3.4) overflows through the reversing buffer valve group (2) to reduce the system flow, the piston movement speed of the pumping main cylinders (3.3, 3.4) is reduced, and part of the hydraulic oil in the oil supply path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) to trigger a second working state of the pumping main cylinders (3.3, 3.4); in a second working state of the pumping master cylinders (3.3, 3.4), supplying hydraulic oil in an oil supply oil path (P11) of the second pressure oil source (P2) to the swing cylinder (1) to move a piston of the swing cylinder (1) in a second direction;
when the piston moves to a second preset reversing position, one part of control oil in a control oil path (P22) of the first pressure oil source (P1) is conveyed to the swing oil cylinder reversing valve group (3.1) to trigger the reversing of the piston, the other part of the control oil in the control oil path (P22) of the first pressure oil source (P1) is conveyed to the reversing buffer valve group (2), part of hydraulic oil flowing to the pumping main oil cylinders (3.3, 3.4) overflows through the reversing buffer valve group (2) to reduce the system flow, the piston movement speed of the main oil pump is reduced, and part of the hydraulic oil in an oil supply oil path (P11) of the first pressure oil source (P1) is conveyed to the pumping system combination (3) to trigger the pumping main oil cylinders (3.3, 3.4) to return to a first working state.
9. The method of claim 8, wherein:
the method comprises the following steps: a second pressure oil source (P2) triggers a first position of the reversing valve group (3.1) to convey hydraulic oil of the second pressure oil source (P2) to a rodless cavity of the first pumping oil cylinder (3.3) through the first branch, a piston of the first pumping oil cylinder (3.3) moves, when the piston moves to a first preset position away from the bottom of the rod cavity, the first pumping oil cylinder (3.3) sends a first hydraulic oil signal to the comparison valve group (3.2), the comparison valve group (3.2) is opened to convey a part of hydraulic oil of a control oil path (P22) of the first pressure oil source (P1) to the swing oil cylinder reversing valve group (3.1), and the swing oil cylinder reversing valve group (3.1) reverses the piston of the swing oil cylinder (1); meanwhile, the other part of hydraulic oil is conveyed to the reversing buffer valve group (2) to overflow;
a second pressure oil source (P2) triggers a second position of the reversing valve group (3.1) to convey hydraulic oil of the second pressure oil source (P2) to a rodless cavity of the second pumping cylinder (3.4) through the second branch, a piston of the second pumping cylinder (3.4) moves, when the piston moves to a second preset position away from the bottom of the rod cavity, the second pumping cylinder (3.4) sends a second hydraulic oil signal to the comparison valve group (3.2), the comparison valve group (3.2) is opened to convey a part of hydraulic oil of a control oil path (P22) of the second pressure oil source (P2) to the swing cylinder reversing valve group (3.1), and the swing cylinder reversing valve group (3.1) reverses the piston of the swing cylinder (1); meanwhile, the other part of hydraulic oil is conveyed to the reversing buffer valve group (2) to overflow.
10. The method of claim 9,
the first preset distance is located between a first outlet (a) and a second outlet (b), and the distance between the first outlet and the second outlet is larger than the thickness of the piston;
the second predetermined distance is located between the third and fourth outlets, and the distance between the third and fourth outlets is greater than the thickness of the piston.
11. The method of claim 10,
when the piston of the first pumping oil cylinder (3.3) is positioned between the first outlet (a) and the second outlet (b), the first comparison valve (3.2.1) is triggered, hydraulic oil of the first oil path triggers the swing oil cylinder reversing valve set (3.1) to reverse the swing oil cylinder (1), and the second oil path triggers the reversing buffer valve set (2) to overflow;
when the piston of the second pumping oil cylinder (3.4) is located between the third outlet (c) and the fourth outlet (d), the second comparison valve (3.2.2) is triggered, hydraulic oil of the third oil way triggers the swing oil cylinder reversing valve set (3.1) to reverse the swing oil cylinder (1), and hydraulic oil of the fourth oil way triggers the reversing buffer valve set (2) to overflow.
12. A pump comprising a hydraulic control system as claimed in any one of claims 1 to 6.
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| CN109340199A (en) * | 2018-12-03 | 2019-02-15 | 三汽车制造有限公司 | Pumping machine hydraulic system |
| CN111456976A (en) * | 2020-05-27 | 2020-07-28 | 徐州徐工施维英机械有限公司 | Pumping machinery hydraulic system and pumping machinery |
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| CN111963509A (en) * | 2020-08-25 | 2020-11-20 | 天津捷强动力装备股份有限公司 | Pressure relief system of pilot oil of oscillating cylinder hydraulic control valve |
| CN113606204A (en) * | 2021-06-17 | 2021-11-05 | 徐州徐工施维英机械有限公司 | Pumping main oil cylinder, control system thereof and equipment applying oil cylinder and system |
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