CN216554321U - Total power control system of hydraulic plunger variable dual pump - Google Patents
Total power control system of hydraulic plunger variable dual pump Download PDFInfo
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- CN216554321U CN216554321U CN202122895836.0U CN202122895836U CN216554321U CN 216554321 U CN216554321 U CN 216554321U CN 202122895836 U CN202122895836 U CN 202122895836U CN 216554321 U CN216554321 U CN 216554321U
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Abstract
The utility model discloses a total power control system of a hydraulic plunger variable double pump, which is characterized in that a first throttling plug and a second throttling plug are connected in series at the outlet pressure oil positions of a first pump and a second pump of the hydraulic plunger variable double pump, the average pressure of the outlet pressure oil of the first pump and the outlet pressure oil of the second pump is obtained through the action of the two throttling plugs, and the average pressure is respectively acted on a constant power control valve of a corresponding total power control valve of the hydraulic plunger variable double pump, so that the output flow of the first pump and the output flow of the second pump are reduced or increased, the total power of the first pump and the total power of the second pump are kept constant, and the total power control of the hydraulic plunger variable double pump is realized. The integral control oil way is simple, easy to process and small in part volume. In conclusion, the utility model has the characteristics of simplifying oil passages, reducing processing difficulty and reducing cost.
Description
Technical Field
The utility model relates to a hydraulic plunger variable displacement duplex pump, in particular to a total power control system of the hydraulic plunger variable displacement duplex pump.
Background
In the hydraulic plunger pump matched with the engineering machinery for use, the constant power control is very widely applied, and the hydraulic plunger variable pump controlled by the constant power can automatically adjust the output flow of the hydraulic plunger variable pump along with the change of load pressure when the engineering machinery executes a plurality of actions, so that the output power of an engine is utilized to the maximum extent.
For the hydraulic plunger variable single pump, the constant power control can be realized relatively simply through the combined action of the outlet pressure signal of the hydraulic plunger variable pump and the control valve. However, in the current engineering machinery, such as an excavator, a crane, etc., a hydraulic plunger variable dual pump is often used, that is, two hydraulic plunger variable dual pumps are used in parallel or in series, in order to control the total power of the hydraulic plunger variable dual pump not to exceed the output power of the engine, it is necessary to perform constant power control on the two hydraulic plunger variable pumps of the hydraulic plunger variable dual pump at the same time, if a control method of the hydraulic plunger variable single pump is adopted, only the respective maximum powers of the two hydraulic plunger variable pumps in the hydraulic plunger variable dual pump can be limited, and the problem that when one hydraulic plunger variable pump consumes less power, the output power of the engine cannot be utilized to the maximum extent by the other hydraulic plunger variable pump cannot be solved. For example: the output power of the engine is 100kW, the maximum power of a first pump in the hydraulic plunger variable dual pump is set to be 60kW, the maximum power of a second pump in the hydraulic plunger variable dual pump is set to be 40kW, the first pump and the second pump can achieve the purpose that the consumed power does not exceed 60kW and 40kW through respective constant power control, and the total power does not exceed 100 kW. If the second pump consumes little power because of a small load, the engine output is mainly consumed by the first pump, but the first pump has a maximum power of only 60kW, so that the engine output cannot be fully utilized; if the second pump consumes less power due to a smaller load, the first pump can consume more engine power, and is not limited to 60kW, so that the engine output power can be utilized to the maximum extent, and the hydraulic plunger variable dual pump constant power control method capable of utilizing the engine output power to the maximum extent is called total power control.
In order to solve the problems, the total power control of the hydraulic plunger variable dual pump in the current market mostly adopts the constant power linkage control of a first pump and a second pump, the pressure signal of the outlet of the first pump acts on a self power control valve and also acts on a constant power control valve of the second pump, the pressure signal of the outlet of the second pump acts on the constant power control valve of the first pump and the total power control valve of the hydraulic plunger variable dual pump, a three-step control valve core is adopted, the constant power control valve core is usually matched with a constant power control valve sleeve, the coaxiality requirement of the diameter of three steps of the constant power control valve core is higher, the coaxiality requirement of an inner hole of the three steps of the constant power control valve sleeve is also higher, otherwise, the power control valve core is acted by a hydraulic clamping force to cause the movement jamming of the power control valve core even jamming and failure of the total power control, the engine has speed reduction and even flameout. The machining of the valve sleeve of the power control valve core is a great challenge, pressure oil at the outlets of the first pump and the second pump needs to be guided to the step part of the constant-power control valve core of the other side in a crossed manner, the oil circuit is complex, the layout and machining of the oil circuit have great difficulty, and the volume of a part machined with the oil circuit can be increased. Therefore, the prior art has the problems of complex oil circuit and large processing difficulty.
SUMMERY OF THE UTILITY MODEL
The utility model aims to provide a total power control system of a hydraulic plunger variable dual pump. The utility model has the characteristics of simplifying oil circuit, reducing processing difficulty and reducing cost.
The technical scheme of the utility model is as follows: a total power control system of a hydraulic plunger variable dual pump comprises a first pump and a second pump, wherein the first pump and the second pump are respectively provided with a first pump outlet oil way and a second pump outlet oil way, the first pump outlet oil way and the second pump outlet oil way are respectively connected with a variable piston and a total power control valve, and the variable piston is matched with the total power control valve; and a first throttling plug and a second throttling plug are also connected in series between the first pump outlet oil way and the second pump outlet oil way, and a control oil way communicated with the total power control valve is arranged between the first throttling plug and the second throttling plug.
In the total power control system of the hydraulic plunger variable displacement dual pump, the total power control valve comprises a constant power control secondary regulating mechanism, a constant power control primary regulating mechanism, a control spring, a servo valve and a constant power control valve which are matched with each other.
In the total power control system of the hydraulic plunger variable displacement dual pump, the control spring comprises a constant power control primary spring, a constant power control secondary spring and a spring seat which are matched with each other.
In the total power control system of the hydraulic plunger variable displacement dual pump, the constant power control valve comprises a constant power control valve sleeve and a constant power control valve core which are of a double-step or stepless structure; the constant power control valve sleeve is linked with the variable piston, and the constant power control valve core is communicated with the control oil way.
In the total power control system of the hydraulic plunger variable displacement dual pump, the servo valve comprises a variable control valve sleeve and a variable control valve core which are matched with each other.
Compared with the prior art, the average pressure of the first pump and the second pump of the hydraulic plunger variable dual pump is obtained through the throttling plug, and acts on the constant power control valve, so that the output flow of the first pump and the output flow of the second pump are reduced or increased, the total power of the first pump and the second pump is kept constant, and the total power control of the hydraulic plunger variable dual pump is realized. The integral control oil way is simple, easy to process and small in part volume. Meanwhile, the utility model adopts two constant power control valve core and valve sleeve structures of double steps or no steps, realizes the total power control of the hydraulic plunger variable dual pump, greatly reduces the processing difficulty of parts, improves the reliability of the total power control, has smaller hydraulic pressure clamp and hydraulic damping in the actual working process, has better variable response characteristic for the constant power control, and has better stability of the total power control. In conclusion, the utility model has the characteristics of simplifying oil paths, reducing processing difficulty and reducing cost.
Drawings
FIG. 1 is a hydraulic schematic diagram for the total power control of a hydraulic plunger variable displacement twin pump according to the present invention;
FIG. 2 is a structural view of a hydraulic plunger variable displacement dual pump total power control valve of a double step structure of the present invention;
fig. 3 is a structural view of the total power control valve of the hydraulic plunger variable displacement dual pump with a stepless structure.
The labels in the figures are: 1-a first pump, 2-a variable piston, 3-a constant power control valve sleeve, 4-a constant power control valve core, 5-a constant power control spring, 6-a first pump outlet oil way, 7-a second pump outlet oil way, 8-a second pump, 9-a first throttle plug, 10-a second throttle plug, 11-a constant power control two-stage adjusting mechanism, 12-a constant power control one-stage adjusting mechanism, 13-a constant power control one-stage spring, 14-a constant power control two-stage spring, 15-a spring seat, 16-a variable control valve sleeve, 17-a variable control valve core, 18-a first oil way, 19-a second oil way, 20-a third oil way and 21-a fourth oil way; 22-fifth oil path.
Detailed Description
The utility model is further illustrated by the following figures and examples, which are not to be construed as limiting the utility model.
Examples are given. A first throttling plug and a second throttling plug are connected in series at the outlet pressure oil positions of a first pump and a second pump of the hydraulic plunger variable dual pump, the average pressure of the outlet pressure oil of the first pump and the outlet pressure oil of the second pump is obtained through the action of the two throttling plugs, and the average pressure is respectively acted on the constant power control valves of the total power control valves of the corresponding hydraulic plunger variable dual pump, so that the total power control of the hydraulic plunger variable dual pump is realized.
The constant power control valve adopts a double-step or stepless constant power control valve.
A total power control system of a hydraulic plunger variable dual pump is formed as shown in figures 1 to 3 and comprises a first pump 1 and a second pump 8, wherein the first pump 1 and the second pump 8 are respectively provided with a first pump outlet oil path 6 and a second pump outlet oil path 7, the first pump outlet oil path 6 and the second pump outlet oil path 7 are respectively connected with a variable piston 2 and a total power control valve, and the variable piston 2 is matched with the total power control valve; a first throttling plug 9 and a second throttling plug 10 are also connected in series between the first pump outlet oil path 6 and the second pump outlet oil path 7, and a control oil path communicated with the total power control valve is arranged between the first throttling plug 9 and the second throttling plug 10.
The total power control valve comprises a constant power control secondary regulating mechanism 11, a constant power control primary regulating mechanism 12, a control spring 5, a servo valve and a constant power control valve which are matched with each other.
The control spring 5 comprises a constant power control primary spring 13, a constant power control secondary spring 14 and a spring seat 15 which are matched with each other.
The constant power control valve comprises a constant power control valve sleeve 3 and a constant power control valve core 4 which are of a double-step or stepless structure; the constant power control valve sleeve 3 is linked with the variable piston 2, and the constant power control valve core 4 is communicated with the control oil way.
The servo valve includes a variable control valve sleeve 16 and a variable control valve spool 17 that cooperate with each other.
The first pump 1 and the second pump 8 of the hydraulic plunger variable dual pump are identical in structure, displacement control is achieved through movement of the variable piston 2, the variable piston 2 is provided with a variable piston large end and a variable piston small end, the small end of the variable piston 2 is normally communicated with the first pump outlet oil way 6 or the second pump outlet oil way 7, and oil communication of the large end of the variable piston 2 is determined by a constant power control valve. The constant power control valve is composed of a constant power control valve sleeve 3 and a constant power control valve core 4 and is a three-position four-way structure valve, the constant power control valve sleeve 3 and the variable piston 2 are in linkage relation, namely when the variable piston 2 moves, the constant power control valve sleeve 3 can be caused to move correspondingly, one end of the constant power control valve core 4 is acted by pressure oil of the first pump outlet oil path 6 and the second pump outlet oil path 7, and the other end of the constant power control valve core is acted by the control spring 5.
The oil paths are respectively led out of the first pump outlet oil path 6 and the second pump outlet oil path 7, the first throttling plug 9 and the second throttling plug 10 are respectively connected in series, the average pressure of the first pump outlet oil path 6 and the second pump outlet oil path 7 is obtained under the action of the two throttling plugs, the average pressure acts on the constant power control valve core 4 of the first pump 1 and one end of the constant power control valve core 4 of the second pump 8, and the other end of the constant power control valve core 4 is under the action of the control spring 5.
The control spring 5 uses a constant power control primary spring 13 and a constant power control secondary spring 14, and sets initial elastic forces of the constant power control primary spring 13 and the constant power control secondary spring 14 through a constant power control primary adjusting mechanism 12 and a constant power control secondary adjusting mechanism 11. The constant power control valve sleeve 3 and the constant power control valve core 4 mainly introduce pressure signals of a first pump outlet oil path 6 and a second pump outlet oil path 7 to generate force for moving the constant power control valve core 4, and a servo valve consisting of a variable control valve sleeve 16 and a variable control valve core 17 is adopted for controlling the on-off of oil of the variable piston 2. The acting force of the constant power control spring 5 and the acting force of the constant power control valve core 4 are transmitted through the mechanical contact of the spring seat 15, the variable control valve core 17 and the constant power control valve core 4, and the variable control valve sleeve 16 is linked with the variable piston 2, namely, when the variable piston 2 moves, the variable control valve sleeve 16 is caused to move correspondingly. The first oil path 18 is communicated with the housing cavity, the second oil path 19 is communicated with the large end of the variable piston 2, the third oil path 20 and the fourth oil path 21 are serially provided with a first throttling plug, the fifth oil path 22 is serially provided with a second throttling plug, pressure signals after the fourth oil path 21 and the fifth oil path are averaged are taken to act on the constant power control valve core 4 with a double-step structure, the fourth oil path 21 and the fifth oil path 22 shown in figure 3 are reasonably simplified into a single oil path, wherein the first throttling plug 9 and the second throttling plug 10 are equivalent orifices, the average pressure is P, and then the flow rate is calculated according to an orifice pressure-flow formula
As can be appreciated, the number of,
the constant power control valve sleeve 3 and the constant power control valve core 4 are provided with only two steps, so that the processing difficulty can be greatly reduced, and the coaxiality of cylindrical surfaces of the two steps can be better ensuredThe clamping possibility of the constant power control valve core 4 is reduced, the stability and the reliability of total power control are greatly improved, meanwhile, the total power control oil circuit of the hydraulic plunger variable displacement duplex pump is simplified, the processing difficulty of the oil circuit is reduced, and the volume of the control valve can be effectively reduced. Assuming that the rest parameters are unchanged, the step area difference between Φ d1 and Φ d2 designed for the constant power control spool 4 of the first pump 1 is S1, and the step area difference between Φ d1 and Φ d2 designed for the constant power control spool 4 of the second pump 8 is S2, then in the process of total power control, the following relations exist:
from the foregoing, S is known11＝S12，S21＝S22From the equation transformation, S1＝2S11＝2S12，S2＝2S21＝2S22. The flow rate change of the first pump 1 or the second pump 8 caused by the displacement of the constant power control valve spool 4 of each of the first pump 1 and the second pump 8 is defined as the following functional relationship:
Q1＝f(x1)
Q2＝f(x2)
through accurate calculation and reasonable structural dimension design, the stressed area S of the double-step constant-power control valve core 4 is ensured1And S2Satisfies S1＝2S11＝2S12，S2＝2S21＝2S22And the equivalent total power control of the hydraulic plunger variable dual pump can be finally realized:
N＝P1Q1+P2Q2。
when a stepless structure is adopted, as shown in fig. 3, the control principle is similar to the constant power control of the existing hydraulic plunger variable displacement dual pump, and the fourth oil path 21 is connected in seriesThe first throttling plug 9 and the fifth oil path 22 are provided with the second throttling plug 10 in series, the pressure signal after the fourth oil path 21 and the fifth oil path 22 are averaged is taken to act on the tail part of the constant power control valve core 4 with the stepless structure, the fourth oil path 21 and the fifth oil path 22 are reasonably simplified into a single oil path, wherein the first throttling plug and the second throttling plug are equivalent throttling holes, the average pressure is P, and then the pressure and flow formula of the throttling holes is obtained according to the pressure and flow formula of the throttling holes
As can be appreciated, the number of,
the constant power control valve sleeve 3 and the constant power control valve core 4 have no steps, so that the processing difficulty can be greatly reduced, only the fit clearance and the roundness of the constant power control valve sleeve 3 and the constant power control valve core 4 need to be ensured, the coaxiality requirement of a cylindrical surface does not exist, the possibility of clamping stagnation of the constant power control valve core 4 can be greatly reduced, the stability and the reliability of total power control are greatly improved, meanwhile, the total power control oil circuit of the hydraulic plunger variable dual pump is simplified, the processing difficulty of the oil circuit is reduced, and the volume of the control valve can be effectively reduced. Assuming the remaining parameters are unchanged, the constant power control valve spool 4 of the first pump 1 is designed to have a diameter Φ d1 with an area S1The area difference of the designed diameter phi d1 of the constant power control valve core 4 of the second pump 8 is S2Then, in the total power control process, there is the following relationship:
from the foregoing, S is known11＝S12，S21＝S22From the equation transformation, S1＝2S11＝2S12，S2＝2S21＝2S22. Since the first pump 1 and the second pump 8 are eachThe flow rate change of the first pump 1 or the second pump 8 caused by the displacement of the self-constant power control valve core 4 is defined as the following functional relation:
Q1＝f(x1)
Q2＝f(x2)
through accurate calculation and reasonable diameter size design of the constant-power control valve core 4, the stress areas S1 and S2 of the stepless constant-power control valve core 4 meet S1＝2S11＝2S12，S2＝2S21＝2S22And the equivalent total power control of the hydraulic plunger variable dual pump can be finally realized:
N＝P1Q1+P2Q2。
Claims (5)
1. the utility model provides a hydraulic plunger variable dual pump total power control system which characterized in that: the variable displacement pump comprises a first pump (1) and a second pump (8), wherein the first pump (1) and the second pump (8) are respectively provided with a first pump outlet oil way (6) and a second pump outlet oil way (7), the first pump outlet oil way (6) and the second pump outlet oil way (7) are respectively connected with a variable piston (2) and a total power control valve, and the variable piston (2) is matched with the total power control valve; and a first throttling plug (9) and a second throttling plug (10) are also connected in series between the first pump outlet oil way (6) and the second pump outlet oil way (7), and a control oil way communicated with the total power control valve is arranged between the first throttling plug (9) and the second throttling plug (10).
2. The hydraulic ram variable displacement tandem pump total power control system of claim 1, wherein: the total power control valve comprises a constant power control secondary regulating mechanism (11), a constant power control primary regulating mechanism (12), a control spring (5), a servo valve and a constant power control valve which are matched with each other.
3. A hydraulic ram variable displacement tandem pump total power control system according to claim 2, wherein: the control spring (5) comprises a constant power control primary spring (13), a constant power control secondary spring (14) and a spring seat (15) which are matched with each other.
4. The hydraulic ram variable displacement tandem pump total power control system of claim 1, wherein: the constant power control valve comprises a constant power control valve sleeve (3) and a constant power control valve core (4) which are of a double-step or no-step structure; the constant power control valve sleeve (3) is linked with the variable piston (2), and the constant power control valve core (4) is communicated with the control oil way.
5. The hydraulic ram variable displacement tandem pump total power control system of claim 1, wherein: the servo valve comprises a variable control valve sleeve (16) and a variable control valve core (17) which are matched with each other.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202122895836.0U CN216554321U (en) | 2021-11-24 | 2021-11-24 | Total power control system of hydraulic plunger variable dual pump |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202122895836.0U CN216554321U (en) | 2021-11-24 | 2021-11-24 | Total power control system of hydraulic plunger variable dual pump |
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| CN216554321U true CN216554321U (en) | 2022-05-17 |
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Address after: 29 Caohu Avenue, Xiangcheng District, Suzhou, Jiangsu Province Patentee after: Suzhou Liyuan Hydraulic Co.,Ltd. Address before: 29 Caohu Avenue, Xiangcheng District, Suzhou, Jiangsu Province Patentee before: LIYUAN HYDRAULIC (SUZHOU) Co.,Ltd. |