CN109914518B - Device for improving dynamic matching performance of power of large excavator - Google Patents
Device for improving dynamic matching performance of power of large excavator Download PDFInfo
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- CN109914518B CN109914518B CN201910186931.8A CN201910186931A CN109914518B CN 109914518 B CN109914518 B CN 109914518B CN 201910186931 A CN201910186931 A CN 201910186931A CN 109914518 B CN109914518 B CN 109914518B
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Abstract
The invention relates to a device for improving power dynamic matching of a large excavator, which comprises a hydraulic control proportional valve, a pressure oil source and a throttling device, wherein the hydraulic control proportional valve is arranged on a main pump negative feedback loop, the main pump negative feedback loop comprises a point a and a point b, negative feedback pressure oil flows from the point a to the point b, the hydraulic control proportional valve is arranged between the point a and the point b, an oil inlet of the hydraulic control proportional valve is connected with the pressure oil source, an oil outlet of the hydraulic control proportional valve is communicated with a main pump through the point b, and a hydraulic control port of the hydraulic control proportional valve is connected with the point a of the main pump negative feedback loop through the throttling device. The device is hydraulic control, has the function of opening and closing in a delayed mode, and solves the problem that the instantaneous power of an engine and a main pump of a large excavator is not matched.
Description
Technical Field
The invention relates to a power matching device, in particular to a device for improving the dynamic matching performance of power of a large excavator.
Background
The power of an engine and a main pump of the hydraulic excavator is generally statically matched, and dynamic adjustment is carried out according to the rotating speed, the load condition and the like of the engine in actual operation. In the dynamic adjustment process, the power responsiveness of the engine may not meet the instantaneous power demand of the main pump under the limitation of a turbocharger and a fuel supply system of the engine, and the large excavator is particularly obvious, so that the problems of engine blocking, black smoke emission and the like are caused, and the service performance of the excavator is reduced.
For an excavator adopting a negative flow hydraulic system, a negative flow control signal is only related to the displacement of a main control valve core, and the larger the displacement of the main control valve core is, the smaller the negative flow control signal is, and the larger the displacement of a main pump is. If the engine is in a light load state and the turbocharger speed is low, when the excavator negative flow control signal is suddenly changed and the displacement of the main pump is suddenly increased, the engine may not meet the power demand of the main pump due to slow response.
Disclosure of Invention
The invention provides a device for improving the dynamic matching performance of the power of a large excavator, aiming at solving the problem that the instantaneous power of an engine and a main pump of the large excavator is not matched to cause the engine to be blocked and black smoke to be emitted, wherein the device is controlled hydraulically, has a delayed opening and closing function, is used in parallel with a negative flow feedback loop of an original excavator, and solves the problem that the instantaneous power of the engine and the main pump of the large excavator is not matched.
In order to solve the problems, the invention adopts the technical scheme that: the device for improving the power dynamic matching of the large excavator comprises a hydraulic control proportional valve, a pressure oil source and a throttling device, wherein the hydraulic control proportional valve is arranged on a main pump negative feedback loop, the main pump negative feedback loop comprises a point a and a point b, pressure oil flows to the point b from the point a, the hydraulic control proportional valve is arranged between the point a and the point b, an oil inlet of the hydraulic control proportional valve is connected with the pressure oil source, an oil outlet of the hydraulic control proportional valve is communicated with a main pump through the point b, and a hydraulic control port of the hydraulic control proportional valve is connected with the point a of the main pump negative feedback loop through the throttling device.
Further, a one-way valve is arranged between the point a and the point b.
Further, the throttling device is a throttling valve.
Furthermore, the throttling device comprises a first throttling valve, a first one-way valve, a second throttling valve and a second one-way valve, and a hydraulic control port of the two-position two-way hydraulic control proportional valve is sequentially connected with an outlet of the first throttling valve and an inlet of the first one-way valve; the inlet of the first throttling valve is connected with the outlet of the second one-way valve; the outlet of the first one-way valve is connected with the inlet of the second throttling valve; and the outlet of the second throttling valve is connected with the inlet of the second one-way valve, and the inlet of the second throttling valve is connected with the point a.
Furthermore, a negative feedback overflow valve used for limiting the maximum pressure of the negative feedback loop is arranged on the main pump negative feedback loop.
Further, the main pump leads to the negative feedback overflow valve and the throttle valve through a main valve.
Further, a negative feedback throttle valve is arranged between the point b and the main pump.
Furthermore, the maximum reset force of the spring of the two-position two-way hydraulic control proportional valve is equivalent to the maximum hydraulic acting force of the hydraulic control port.
Further, the maximum pressure of the pressure oil source is equivalent to the maximum pressure of the negative feedback loop.
The working process of the device is as follows:
when the excavator is started and does not act, high-pressure oil of the negative feedback loop enters a hydraulic control port of the two-position two-way hydraulic control proportional valve through the throttle valve, and the high-pressure oil overcomes the spring resetting force of the two-position two-way hydraulic control proportional valve to enable the two-position two-way hydraulic control proportional valve to be completely opened. Since the maximum pressure of the pressure oil source is equivalent to the maximum pressure of the negative feedback loop, the negative feedback pressure received by the main pump is unchanged at the moment.
When the excavator starts to act, the pressure of the negative feedback loop is supposed to be minimum, the two-position two-way hydraulic control proportional valve starts to reset under the action of the spring reset force, but the reset speed is slow due to the throttling action of the throttle valve, so that the outlet pressure of the two-position two-way hydraulic control proportional valve is gradually reduced from the pressure of the pressure oil source to the pressure of the feedback loop. The size of the opening of the throttle valve can be controlled to control the reset speed of the two-position two-way hydraulic control proportional valve, namely the speed of reducing the outlet pressure of the two-position two-way hydraulic control proportional valve. And the outlet of the two-position two-way hydraulic control proportional valve is also directly connected with a negative flow feedback receiving port of the main pump, so that the discharge capacity of the main pump is gradually increased from minimum along with the outlet pressure of the two-position two-way hydraulic control proportional valve, and the aim of adapting to the power response of an engine is fulfilled.
When the excavator does not act from action to action, the pressure of the negative feedback loop is increased from minimum to maximum, at the moment, high-pressure oil of the negative feedback loop enters a hydraulic control opening of the two-position two-way hydraulic control proportional valve slowly due to the throttling function of the throttle valve, the reversing speed of the two-position two-way hydraulic control proportional valve is pushed to be slow, and the opening of the two-position two-way hydraulic control proportional valve is gradually increased. And the high-pressure oil of the negative feedback loop can directly enter the negative flow feedback receiving port of the main pump through the one-way valve, so that the discharge capacity of the main pump is reduced to the minimum.
The beneficial effects produced by the invention comprise: adjusting the negative feedback pressure only within a specified time to match the power response of the engine and the main pump; and a hydraulic control valve is adopted, and complex electric control logic control is not needed.
Drawings
FIG. 1 is a schematic diagram of a connection relationship between a pressure regulating device and a negative feedback loop of a main pump in the present invention;
FIG. 2 is a schematic view showing the structure of a pressure adjusting device in embodiment 1 of the present invention;
fig. 3 is a schematic structural view of a pressure regulating device in embodiment 2 of the present invention.
Detailed Description
The present invention is explained in further detail below with reference to the drawings and the detailed description, but it should be understood that the scope of the present invention is not limited by the detailed description.
Example 1
As shown in fig. 1-2, the device for improving power dynamic matching of a large excavator in the present invention includes a pilot-controlled proportional valve, a pressure oil source and a throttle valve, the pilot-controlled proportional valve is disposed on a main pump negative feedback loop, the main pump negative feedback loop includes a point a and a point b, pressure oil flows from the point a to the point b, a pressure adjusting device is connected in parallel with an oil path between the point a and the point b, the pilot-controlled proportional valve is disposed between the point a and the point b, an oil inlet of the pilot-controlled proportional valve is connected to the pressure oil source, an oil outlet of the pilot-controlled proportional valve is led to the main pump through the point b, a pilot-controlled port of the pilot-controlled proportional valve is connected to the point a of the main pump negative feedback loop through the throttle valve, and a check valve for ensuring one-way flow of the pressure oil from the point a to the point b is disposed between the point a and the point b. The maximum reset force of the spring of the two-position two-way hydraulic control proportional valve is equivalent to the maximum acting force of hydraulic pressure of the hydraulic control port. The maximum pressure of the pressure oil source is equivalent to the maximum pressure of the negative feedback loop. When the two-position two-way hydraulic control proportional valve works, the oil outlet is opened. And a negative feedback overflow valve used for limiting the maximum pressure of the negative feedback loop is arranged on the negative feedback loop of the main pump. The main pump leads to a negative feedback overflow valve and a throttle valve through a main valve. And a negative feedback throttle valve is arranged between the point b and the main pump.
The working process of the device is as follows:
firstly, when the excavator is started and does not act, oil discharged by the main pump 6 enters the inlets of the negative feedback overflow valve 9 and the negative feedback throttle valve 10 through the main control valve 7. The negative feedback overflow valve 9 is used to limit the maximum pressure of the negative feedback loop. The pressure at the inlet of the negative feedback throttle 10 is a negative feedback pressure, and a higher oil pressure is formed at the inlet due to the damping action of the negative feedback throttle 10. High-pressure oil at the inlet of the negative feedback throttle valve 10 enters a hydraulic control port of the two-position two-way hydraulic control proportional valve 1 through the throttle valve 3, and the high-pressure oil overcomes the spring resetting force of the two-position two-way hydraulic control proportional valve 1 to enable the two-position two-way hydraulic control proportional valve 1 to be completely opened. Since the maximum pressure of the pressure oil source 4 is equivalent to the maximum pressure of the negative feedback loop, the negative feedback pressure received by the main pump displacement adjusting structure 5 is unchanged, and the displacement of the main pump 6 is unchanged and is maintained at the minimum.
Secondly, when the excavator starts to act, the main control valve 7 is reversed, oil discharged by the main pump does not enter the negative feedback throttle valve 10 any more, and the negative feedback pressure reaches the minimum. The pressure of oil entering the hydraulic control port of the two-position two-way hydraulic control proportional valve 1 through the throttle valve 3 is reduced, the two-position two-way hydraulic control proportional valve 1 starts to reset under the action of the spring reset force, but the reset speed is slow due to the throttling action of the throttle valve 3, so that the outlet pressure of the two-position two-way hydraulic control proportional valve 1 is gradually reduced to negative feedback pressure from the pressure of the pressure oil source 4. The opening of the throttle valve 3 can be controlled to control the reset speed of the two-position two-way hydraulic control proportional valve 1, namely the speed of reducing the outlet pressure of the two-position two-way hydraulic control proportional valve 1. And the outlet of the two-position two-way hydraulic control proportional valve 1 is also directly connected with the main pump displacement adjusting structure 5. Therefore, at the initial time when the pressure at the inlet of the negative feedback throttle valve 10 is reduced to the minimum, the outlet pressure of the two-position, two-way pilot-controlled proportional valve 1 is still maintained at a high pressure, and the main pump displacement adjustment mechanism 5 is still maintaining the displacement of the main pump 6 at a small displacement. Along with the gradual reduction of the opening of the two-position two-way hydraulic control proportional valve 1, the outlet pressure of the two-position two-way hydraulic control proportional valve 1 is gradually reduced from the maximum, the discharge capacity of the main pump 6 is gradually increased, and the purpose that the power response time of the main pump 6 is adaptive to the power response time of an engine is achieved.
Thirdly, when the excavator does not act from action to non-action, the pressure at the inlet of the negative feedback throttle valve 10 is increased from minimum to maximum, at the moment, due to the throttling action of the throttle valve 3, the speed of negative feedback high-pressure oil entering the hydraulic control port of the two-position two-way hydraulic control proportional valve 1 is slower, the reversing speed of pushing the two-position two-way hydraulic control proportional valve 1 is slower, and the opening of the two-position two-way hydraulic control proportional valve 1 is gradually increased. And negative feedback high-pressure oil can directly enter the main pump displacement adjusting mechanism 5 through the one-way valve 2 to adjust the displacement of the main pump 6 to the minimum.
Fourthly, the main control valve 7 starts to act again in a very short time after the displacement of the main pump 6 is reduced, and at the moment, because of the short time, the valve core of the two-position two-way pilot control proportional valve 1 is still maintained at the closed position. And the engine turbocharger is also maintained at a high rotating speed, the engine power response can still meet the response requirement of the main pump, and the displacement of the main pump 6 is changed according to the normal speed.
Example 2
The throttle valve 3 is modified to set the times at which the two-position, two-way pilot-controlled proportional valve 1 opens and closes, respectively, as compared with embodiment 1. The concrete structure is as follows: a hydraulic control port of the two-position two-way hydraulic control proportional valve 1 is connected with an outlet of a first throttling valve 3.1 and an inlet of a first one-way valve 3.2; the inlet of the first throttle valve 3.1 is connected with the outlet of the second one-way valve 3.4; the outlet of the first one-way valve 3.2 is connected with the inlet of the second throttling valve 3.3; the outlet of the second throttling valve 3.3 is connected with the inlet of a second check valve 3.4 and the inlet of the check valve 2. In this way, the throttle areas of the first throttle valve 3.1 and the second throttle valve 3.3 are different, so that the opening and closing times of the two-position two-way hydraulic control proportional valve 1 are different, and the requirements of different adjustment times of the displacement of the main pump 6 from large to small and from small to large are met.
The above description is only a preferred embodiment of the present invention, and the present invention is not limited to the content of the embodiment. It will be apparent to those skilled in the art that various changes and modifications can be made within the technical scope of the present invention, and any changes and modifications made are within the protective scope of the present invention.
Claims (2)
1. The utility model provides a promote device of large-scale excavator power dynamic matching nature which characterized in that: the hydraulic control proportional valve is arranged on a main pump negative feedback loop, the main pump negative feedback loop comprises a point a and a point b, negative feedback pressure oil flows from the point a to the point b, the hydraulic control proportional valve is arranged between the point a and the point b, an oil inlet of the hydraulic control proportional valve is connected with the pressure oil source, an oil outlet of the hydraulic control proportional valve is communicated with a main pump through the point b, and a hydraulic control port of the hydraulic control proportional valve is connected with the point a of the main pump negative feedback loop through a throttling device; a one-way valve is arranged between the point a and the point b; a negative feedback overflow valve for limiting the maximum pressure of the negative feedback loop is arranged on the negative feedback loop of the main pump; a negative feedback throttle valve is arranged between the point b and the main pump; the main pump is communicated with the negative feedback overflow valve and the negative feedback throttle valve through a main valve; the hydraulic control proportional valve is a two-position two-way hydraulic control proportional valve, and the maximum reset force of a spring of the two-position two-way hydraulic control proportional valve is equivalent to the maximum hydraulic acting force of the hydraulic control port;
the throttling device comprises a first throttling valve, a first one-way valve, a second throttling valve and a second one-way valve, wherein a hydraulic control port of a two-position two-way hydraulic control proportional valve is sequentially connected with an outlet of the first throttling valve and an inlet of the first one-way valve; the inlet of the first throttling valve is connected with the outlet of the second one-way valve; the outlet of the first one-way valve is connected with the inlet of the second throttling valve; and the outlet of the second throttling valve is connected with the inlet of the second one-way valve, and the inlet of the second throttling valve is connected with the point a.
2. The apparatus for improving power dynamic matching of a large excavator according to claim 1, wherein: the maximum pressure of the pressure oil source is equivalent to the maximum pressure of the negative feedback loop.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910186931.8A CN109914518B (en) | 2019-03-13 | 2019-03-13 | Device for improving dynamic matching performance of power of large excavator |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910186931.8A CN109914518B (en) | 2019-03-13 | 2019-03-13 | Device for improving dynamic matching performance of power of large excavator |
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| CN109914518A CN109914518A (en) | 2019-06-21 |
| CN109914518B true CN109914518B (en) | 2022-04-01 |
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| CN110616769B (en) * | 2019-09-26 | 2022-04-15 | 雷沃工程机械集团有限公司 | Negative flow control excavator accessory flow control device and method and excavator |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN200971837Y (en) * | 2006-11-09 | 2007-11-07 | 佛山市顺德区必乐士液压机械有限公司 | Plunger pump |
| JP2008039063A (en) * | 2006-08-07 | 2008-02-21 | Sumitomo (Shi) Construction Machinery Manufacturing Co Ltd | Hydraulic control circuit of construction machine |
| CN102893036A (en) * | 2010-12-28 | 2013-01-23 | 卡特彼勒Sarl公司 | Fluid pressure circuit control apparatus and working machine |
| CN102943500A (en) * | 2012-11-16 | 2013-02-27 | 无锡汇虹机械制造有限公司 | Energy-saving control method of hydraulic negative flow of excavator |
| CN206988194U (en) * | 2017-06-29 | 2018-02-09 | 湖南十开科技有限公司 | A kind of flow prior control loop |
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2019
- 2019-03-13 CN CN201910186931.8A patent/CN109914518B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008039063A (en) * | 2006-08-07 | 2008-02-21 | Sumitomo (Shi) Construction Machinery Manufacturing Co Ltd | Hydraulic control circuit of construction machine |
| CN200971837Y (en) * | 2006-11-09 | 2007-11-07 | 佛山市顺德区必乐士液压机械有限公司 | Plunger pump |
| CN102893036A (en) * | 2010-12-28 | 2013-01-23 | 卡特彼勒Sarl公司 | Fluid pressure circuit control apparatus and working machine |
| CN102943500A (en) * | 2012-11-16 | 2013-02-27 | 无锡汇虹机械制造有限公司 | Energy-saving control method of hydraulic negative flow of excavator |
| CN206988194U (en) * | 2017-06-29 | 2018-02-09 | 湖南十开科技有限公司 | A kind of flow prior control loop |
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