CN113153136A - Power head pressurizing force control method and system and rotary drilling rig - Google Patents
Power head pressurizing force control method and system and rotary drilling rig Download PDFInfo
- Publication number
- CN113153136A CN113153136A CN202110367649.7A CN202110367649A CN113153136A CN 113153136 A CN113153136 A CN 113153136A CN 202110367649 A CN202110367649 A CN 202110367649A CN 113153136 A CN113153136 A CN 113153136A
- Authority
- CN
- China
- Prior art keywords
- control coefficient
- power head
- torque
- pressure
- pressure control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000000034 method Methods 0.000 title claims abstract description 26
- 238000005553 drilling Methods 0.000 title claims abstract description 8
- 238000006073 displacement reaction Methods 0.000 claims description 42
- 238000001514 detection method Methods 0.000 claims description 15
- 238000004364 calculation method Methods 0.000 claims description 7
- 230000005540 biological transmission Effects 0.000 claims description 4
- 238000010276 construction Methods 0.000 abstract description 4
- 238000003466 welding Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
Images
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B3/00—Rotary drilling
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B44/00—Automatic control systems specially adapted for drilling operations, i.e. self-operating systems which function to carry out or modify a drilling operation without intervention of a human operator, e.g. computer-controlled drilling systems; Systems specially adapted for monitoring a plurality of drilling variables or conditions
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B45/00—Measuring the drilling time or rate of penetration
Landscapes
- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Physics & Mathematics (AREA)
- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Mechanical Engineering (AREA)
- Control Of Electric Motors In General (AREA)
Abstract
The embodiment of the invention provides a power head pressurizing force control method and system and a rotary drilling rig, and belongs to the technical field of hydraulic control. The power head pressure control method comprises the following steps: determining a pressurizing force control coefficient according to the torque of the power head and/or the rotating speed of the power head; controlling the pressurizing force according to the pressurizing force control coefficient. According to the method, the torque of the power head and the rotating speed of the power head are used for controlling the pressurizing force of the power head in a correlation mode, the power requirements under various working conditions can be effectively matched, and the influence on the construction efficiency due to the fact that the pressurizing force is not adjusted in real time is avoided.
Description
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a power head pressurizing force control method and system and a rotary drilling rig.
Background
The torque of the power head is related to the load and the pressure of the power head, and when the pressure of the power head is large, the drill cannot be held due to the fact that the torque of the power head is also large. However, the torque actually output by the power head is limited, so that the pressure applied to the power head needs to be controlled in order to prevent the pressure-holding drilling phenomenon.
In the prior art, the means for controlling the pressurizing force of the power head is to control the pressure of a main oil way or the horizontal angle of equipment for rotating the power head, and the control effect is not ideal.
Disclosure of Invention
The embodiment of the invention aims to provide a method which utilizes the torque of a power head and the rotating speed of the power head to control the pressurizing force of the power head in a correlation manner, can effectively match the power requirements under various working conditions, and avoids the influence on the construction efficiency due to the fact that the pressurizing force is not adjusted in real time.
In order to achieve the above object, an embodiment of the present invention provides a power head pressure control method, including: determining a pressurizing force control coefficient according to the torque of the power head and/or the rotating speed of the power head; controlling the pressurizing force according to the pressurizing force control coefficient.
Optionally, the determining a pressure control coefficient according to the power head torque and/or the power head rotation speed includes: determining a torque-pressure control coefficient and/or a rotation speed-pressure control coefficient; and determining a pressurizing force control coefficient according to the torque-pressurizing force control coefficient and/or the rotating speed-pressurizing force control coefficient.
Optionally, the determining a welding pressure control coefficient according to the torque-welding pressure control coefficient and/or the rotation speed-welding pressure control coefficient includes: taking the torque-pressure control coefficient or the rotation speed-pressure control coefficient as the pressure control coefficient; alternatively, the result of the integrated calculation of the torque-applied pressure control coefficient and the rotation speed-applied pressure control coefficient is taken as the applied pressure control coefficient.
Alternatively, the torque-to-pressure force control coefficient is determined according to the following manner: acquiring the driving pressure and the motor displacement of the power head; calculating the torque of the power head according to the driving pressure and the motor displacement; determining a torque-pressure control coefficient according to the torque of the power head, wherein the torque-pressure control coefficient satisfies the following conditions: the larger the torque of the power head, the smaller the pressurizing force.
Optionally, the power head torque is calculated according to the following formula:
wherein T is the power head torque, P is the driving pressure, V is the motor displacement, pi is the circumferential rate, and eta is the transmission efficiency.
Alternatively, the torque-to-pressure force control coefficient is determined according to the following manner: acquiring the driving pressure and the motor displacement of the power head; determining a driving pressure-pressure control coefficient according to the driving pressure, wherein the driving pressure-pressure control coefficient satisfies the following conditions: the larger the driving pressure, the smaller the pressurizing force, and determining a motor displacement-pressurizing force control coefficient according to the motor displacement, the motor displacement-pressurizing force control coefficient satisfying: the larger the motor displacement is, the smaller the pressurizing force is; determining the torque-to-pressure control coefficient based on the drive pressure-to-pressure control coefficient and the motor displacement-to-pressure control coefficient.
Alternatively, the rotation speed-pressure control coefficient is determined according to the following manner: acquiring the rotating speed of the power head; determining a rotation speed-pressure control coefficient according to the rotation speed of the power head, wherein the rotation speed-pressure control coefficient meets the following requirements: the lower the power head rotation speed, the lower the pressurizing force.
In another aspect, the present invention provides a power head pressurization control system, including: the power head driving pressure detection device is used for acquiring the power head driving pressure; the power head motor displacement detection device is used for acquiring the power head motor displacement, and the power head driving pressure and the power head motor displacement are used for determining the power head torque; the power head rotating speed detection device is used for acquiring the rotating speed of the power head; and the controller is used for determining a pressurizing force control coefficient according to the power head torque and/or the power head rotating speed and controlling the pressurizing force according to the pressurizing force control coefficient.
Optionally, the determining a pressure control coefficient according to the power head torque and/or the power head rotation speed includes: determining a torque-pressure control coefficient and/or a rotation speed-pressure control coefficient; and determining a pressurizing force control coefficient according to the torque-pressurizing force control coefficient and/or the rotating speed-pressurizing force control coefficient.
Optionally, the determining a welding pressure control coefficient according to the torque-welding pressure control coefficient and/or the rotation speed-welding pressure control coefficient includes: taking the torque-pressure control coefficient or the rotation speed-pressure control coefficient as the pressure control coefficient; alternatively, the result of the integrated calculation of the torque-applied pressure control coefficient and the rotation speed-applied pressure control coefficient is taken as the applied pressure control coefficient.
Alternatively, the torque-to-pressure force control coefficient is determined according to the following manner: acquiring the driving pressure and the motor displacement of the power head; calculating the torque of the power head according to the driving pressure and the motor displacement; determining a torque-pressure control coefficient according to the torque of the power head, wherein the torque-pressure control coefficient satisfies the following conditions: the larger the torque of the power head, the smaller the pressurizing force.
Alternatively, the torque-to-pressure force control coefficient is determined according to the following manner: acquiring the driving pressure and the motor displacement of the power head; determining a driving pressure-pressure control coefficient according to the driving pressure, wherein the driving pressure-pressure control coefficient satisfies the following conditions: the larger the driving pressure, the smaller the pressurizing force, and determining a motor displacement-pressurizing force control coefficient according to the motor displacement, the motor displacement-pressurizing force control coefficient satisfying: the larger the motor displacement is, the smaller the pressurizing force is; determining the torque-to-pressure control coefficient based on the drive pressure-to-pressure control coefficient and the motor displacement-to-pressure control coefficient.
Alternatively, the rotation speed-pressure control coefficient is determined according to the following manner: acquiring the rotating speed of the power head; determining a rotation speed-pressure control coefficient according to the rotation speed of the power head, wherein the rotation speed-pressure control coefficient meets the following requirements: the lower the power head rotation speed, the lower the pressurizing force.
In another aspect, the invention provides a rotary drilling rig, which comprises the power head pressure force control system according to any one of the above preferred embodiments.
Through the technical scheme, the power head torque and the power head rotating speed are used for controlling the pressurizing force of the power head in a correlation mode, the power requirements under various working conditions can be effectively matched, and the influence on the construction efficiency due to the fact that the pressurizing force is not adjusted in real time is avoided.
Additional features and advantages of embodiments of the invention will be set forth in the detailed description which follows.
Drawings
The accompanying drawings, which are included to provide a further understanding of the embodiments of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the embodiments of the invention without limiting the embodiments of the invention. In the drawings:
fig. 1 is a flowchart of a pressure control method for a power head according to an embodiment of the present invention;
FIG. 2 is a schematic diagram illustrating torque-applied pressure control characteristics according to an embodiment of the present invention;
FIG. 3 is a schematic diagram illustrating rotational speed-applied pressure control characteristics according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of the inverse proportional valve control characteristics provided by one embodiment of the present invention;
fig. 5 is a schematic structural diagram of a pressure control system of a power head according to an embodiment of the present invention.
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating embodiments of the invention, are given by way of illustration and explanation only, not limitation.
The invention provides a power head pressure method, which comprises the following steps of S102-S104:
s102, determining a pressurizing force control coefficient according to the torque of the power head and/or the rotating speed of the power head;
and S104, controlling the pressurizing force according to the pressurizing force control coefficient.
S102 may still further include S1022-S1024:
s1022, the torque-applied pressure control coefficient and/or the rotation speed-applied pressure control coefficient are/is determined.
And S1024, determining a pressurizing force control coefficient according to the torque-pressurizing force control coefficient and/or the rotating speed-pressurizing force control coefficient.
Wherein, S1024 includes three execution modes: and taking the torque-pressure control coefficient as a pressure control coefficient, or taking the rotating speed-pressure control coefficient as a pressure control coefficient, or taking the result of the integrated calculation of the torque-pressure control coefficient and the rotating speed-pressure control coefficient as the pressure control coefficient, wherein the integrated calculation mode comprises algorithms such as multiplication, weighting and the like.
One way of determining the torque-pressure control coefficient includes S202 to S206:
and S202, acquiring the driving pressure and the motor displacement of the power head.
The driving pressure of the power head can be acquired by a power head driving pressure detection device in real time; the motor displacement of the power head can be acquired by a detection device for the motor displacement of the power head in real time, and the specific implementation mode is as follows: the electric control power head motor can reversely calculate the motor displacement according to the control current signal, and the hydraulic control power head motor can calculate the power head displacement (the power head displacement is equal to the hydraulic flow/the power head rotating speed) through the hydraulic flowmeter and the power head rotating speed.
And S204, calculating the torque of the power head according to the driving pressure and the motor displacement.
Specifically, the torque of the power head is calculated according to the following formula:
wherein T is the power head torque, P is the driving pressure, V is the motor displacement, pi is the circumferential rate, and eta is the transmission efficiency.
S206, determining a torque-pressure control coefficient according to the torque of the power head, wherein the torque-pressure control coefficient meets the following requirements: the larger the torque of the power head, the smaller the pressurizing force.
The power head operating characteristic is that the larger the power head torque is, the smaller the allowable pressurizing force is, and therefore, this is taken as a limiting condition of the torque-pressurizing force control coefficient.
FIG. 2 illustrates a torque-to-applied pressure control characteristic in which the applied pressure percentage is maintained at 100% when the powerhead torque does not reach the threshold, decreases with increasing powerhead torque when the powerhead torque exceeds the threshold and is less than a maximum allowable value, and maintains a standby value (which is not necessarily limited to 0) when the powerhead torque reaches the maximum allowable value. Fig. 2 shows only an example of an inverse proportional linear relationship, and the actual torque-pressure control characteristic may be non-linear, but it is necessary to satisfy that the pressurizing force monotonically decreases as the power head torque increases, that is, it is sufficient that the larger the power head torque is, the smaller the pressurizing force is.
Another way of determining the torque-pressure control coefficient includes S302-S306:
and S302, acquiring the driving pressure and the motor displacement of the power head.
And S304, determining a driving pressure-pressurizing force control coefficient according to the driving pressure, and determining a motor displacement-pressurizing force control coefficient according to the motor displacement.
Because the unit head moment of torsion is drive pressure motor discharge capacity, when drive pressure or motor discharge capacity increase, the unit head moment of torsion increase, when drive pressure or motor discharge capacity reduce, the unit head moment of torsion reduces, and drive pressure, motor discharge capacity and unit head moment of torsion have the same monotonicity promptly, need satisfy in view of moment of torsion-pressure control coefficient: the larger the torque of the power head is, the smaller the pressurizing force is, so that the driving pressure-pressurizing force control coefficient also meets the following requirements: the larger the driving pressure, the smaller the pressurizing force, and the motor displacement-pressurizing force control coefficient also satisfies: the larger the motor displacement, the smaller the pressurizing force.
S306, determining the torque-pressure control coefficient according to the driving pressure-pressure control coefficient and the motor displacement-pressure control coefficient.
For example, the driving pressure-to-pressure control coefficient and the motor displacement-to-pressure control coefficient may be calculated as the torque-to-pressure control coefficient by integration, which may include multiplication, weighting, and other algorithms.
The rotation speed-applied pressure control coefficient may be determined according to steps S402-S404:
and S402, acquiring the rotation speed of the power head.
The rotation speed of the power head can be acquired by a power head rotation speed detection device in real time, and for example, the rotation speed detection device can be realized by a rotation speed detection sensor carried by a power head motor or by adding a rotation speed detection sensor on other elements of a power head transmission chain.
S404, determining a rotation speed-pressure control coefficient according to the rotation speed of the power head, wherein the rotation speed-pressure control coefficient meets the following requirements: the lower the power head rotation speed, the lower the pressurizing force.
The power head operating characteristic is that the lower the power head rotation speed is, the smaller the allowable pressurizing force is, and therefore, the lower the allowable pressurizing force is, the limiting condition of the rotation speed-pressurizing force control coefficient is set.
FIG. 3 illustrates a speed-to-pressure control characteristic in which the percent pressure is maintained at a standby value (which is not necessarily limited to 0) when the speed of the powerhead has not reached the minimum allowable value, is increased as the torque of the powerhead increases when the speed of the powerhead exceeds the minimum allowable value and is less than a threshold value, and is maintained at 100% when the speed of the powerhead reaches the threshold value. Fig. 3 shows only one example of a direct-proportional linear relationship, and the actual rotation speed-pressure control characteristic may be non-linear, but it is necessary to satisfy that the pressurizing force monotonically decreases as the rotation speed of the power head decreases, that is, to satisfy that the smaller the rotation speed of the power head, the smaller the pressurizing force.
And S104, controlling the pressurizing force according to the pressurizing force control coefficient.
The execution mode can be that the pressurizing force of the power head is controlled by a hydraulic valve, and the power head can be a continuously controlled proportional valve or a sectionally controlled switch valve. Fig. 4 shows a control characteristic diagram of the hydraulic valve in inverse proportion. When the control signal does not reach 200mA, the percentage of the applied pressure is kept at 100%, when the control signal is in the effective control interval of 200-600 mA, the percentage of the applied pressure is changed from 100% to a standby value (the standby value is not required to be limited to 0), and when the control signal reaches 600mA, the percentage of the applied pressure is kept at the standby value. Fig. 4 shows only the control characteristic of an inversely proportional fully linear hydraulic valve, which may also be a proportional or non-fully linear hardware.
Therefore, the power head pressure control method provided by the embodiment can realize that the pressure is controlled according to the torque of the power head alone and the pressure is controlled according to the rotating speed of the power head alone, and can also realize that the pressure of the power head is controlled by the association of the torque of the power head and the rotating speed of the power head; the association control method can be applied to the scene when the actual rotating speed of the power head is smaller than the theoretical rotating speed (overflow occurs in a hydraulic system).
The present invention also provides a power head pressure force control system, as shown in fig. 5, including: the power head driving pressure detection device is used for acquiring the power head driving pressure; the power head motor displacement detection device is used for acquiring the power head motor displacement, and the power head driving pressure and the power head motor displacement are used for determining the power head torque; the power head rotating speed detection device is used for acquiring the rotating speed of the power head; and a controller for executing the power head pressure force control method according to the above embodiment.
In a preferred embodiment of the present invention, the determining the pressurizing force control coefficient according to the power head torque and/or the power head rotation speed includes:
determining a torque-pressure control coefficient and/or a rotation speed-pressure control coefficient;
and determining a pressurizing force control coefficient according to the torque-pressurizing force control coefficient and/or the rotating speed-pressurizing force control coefficient.
In one preferable embodiment of the present invention, the determining a pressurizing force control coefficient according to the torque-pressurizing force control coefficient and/or the rotation speed-pressurizing force control coefficient includes:
taking the torque-pressure control coefficient or the rotation speed-pressure control coefficient as the pressure control coefficient; alternatively, the result of the integrated calculation of the torque-applied pressure control coefficient and the rotation speed-applied pressure control coefficient is taken as the applied pressure control coefficient.
In a preferred embodiment of the present invention, the torque-to-pressure control coefficient is determined according to the following manner:
acquiring the driving pressure and the motor displacement of the power head;
calculating the torque of the power head according to the driving pressure and the motor displacement;
determining a torque-pressure control coefficient according to the torque of the power head, wherein the torque-pressure control coefficient satisfies the following conditions: the larger the torque of the power head, the smaller the pressurizing force.
In a preferred embodiment of the present invention, the torque-to-pressure control coefficient is determined according to the following manner:
acquiring the driving pressure and the motor displacement of the power head;
determining a driving pressure-pressure control coefficient according to the driving pressure, wherein the driving pressure-pressure control coefficient satisfies the following conditions: the larger the driving pressure, the smaller the pressurizing force, and determining a motor displacement-pressurizing force control coefficient according to the motor displacement, the motor displacement-pressurizing force control coefficient satisfying: the larger the motor displacement is, the smaller the pressurizing force is;
determining the torque-to-pressure control coefficient based on the drive pressure-to-pressure control coefficient and the motor displacement-to-pressure control coefficient.
In a preferred embodiment of the present invention, the rotation speed-pressure control coefficient is determined in accordance with the following manner:
acquiring the rotating speed of the power head;
determining a rotation speed-pressure control coefficient according to the rotation speed of the power head, wherein the rotation speed-pressure control coefficient meets the following requirements: the lower the power head rotation speed, the lower the pressurizing force.
The power head rotating speed and pressure control system controls the pressure of the power head by using the torque of the power head and the rotating speed of the power head in a correlation manner, can effectively match the power requirements under various working conditions, and avoids the influence on the construction efficiency due to the fact that the pressure is not adjusted in real time.
The invention also provides a rotary drilling rig, which comprises the power head pressure control system in any one of the preferred embodiments.
It is to be noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in the process, method, article, or apparatus that comprises the element.
The above are merely examples of the present application and are not intended to limit the present application. Various modifications and changes may occur to those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the scope of the claims of the present application.
Claims (11)
1. A power head pressurization force control method is characterized by comprising the following steps:
determining a pressurizing force control coefficient according to the torque of the power head and/or the rotating speed of the power head;
controlling the pressurizing force according to the pressurizing force control coefficient.
2. The method for controlling the pressure of the power head according to claim 1, wherein the determining the pressure control coefficient according to the torque of the power head and/or the rotating speed of the power head comprises:
determining a torque-pressure control coefficient and/or a rotation speed-pressure control coefficient;
and determining a pressurizing force control coefficient according to the torque-pressurizing force control coefficient and/or the rotating speed-pressurizing force control coefficient.
3. The powerhead pressure control method of claim 2, wherein determining a pressure force control coefficient as a function of the torque-pressure force control coefficient and/or the speed-pressure force control coefficient comprises:
taking the torque-pressure control coefficient or the rotation speed-pressure control coefficient as the pressure control coefficient; alternatively, the result of the integrated calculation of the torque-applied pressure control coefficient and the rotation speed-applied pressure control coefficient is taken as the applied pressure control coefficient.
4. The powerhead pressure control method of claim 2 or 3, wherein the torque-to-pressure control coefficient is determined according to:
acquiring the driving pressure and the motor displacement of the power head;
calculating the torque of the power head according to the driving pressure and the motor displacement;
determining a torque-pressure control coefficient according to the torque of the power head, wherein the torque-pressure control coefficient satisfies the following conditions: the larger the torque of the power head, the smaller the pressurizing force.
5. The powerhead pressure control method of claim 4, wherein the powerhead torque is calculated according to the following equation:
wherein T is the power head torque, P is the driving pressure, V is the motor displacement, pi is the circumferential rate, and eta is the transmission efficiency.
6. The powerhead pressure control method of claim 2 or 3, wherein the torque-to-pressure control coefficient is determined according to:
acquiring the driving pressure and the motor displacement of the power head;
determining a driving pressure-pressure control coefficient according to the driving pressure, wherein the driving pressure-pressure control coefficient satisfies the following conditions: the larger the driving pressure, the smaller the pressurizing force, and determining a motor displacement-pressurizing force control coefficient according to the motor displacement, the motor displacement-pressurizing force control coefficient satisfying: the larger the motor displacement is, the smaller the pressurizing force is;
determining the torque-to-pressure control coefficient based on the drive pressure-to-pressure control coefficient and the motor displacement-to-pressure control coefficient.
7. The power head pressure force control method according to claim 2 or 3, wherein the rotation speed-pressure force control coefficient is determined according to the following manner:
acquiring the rotating speed of the power head;
determining a rotation speed-pressure control coefficient according to the rotation speed of the power head, wherein the rotation speed-pressure control coefficient meets the following requirements: the lower the power head rotation speed, the lower the pressurizing force.
8. A powerhead pressurization control system, comprising:
the power head driving pressure detection device is used for acquiring the power head driving pressure;
the power head motor displacement detection device is used for acquiring the power head motor displacement, and the power head driving pressure and the power head motor displacement are used for determining the power head torque;
the power head rotating speed detection device is used for acquiring the rotating speed of the power head;
and the controller is used for determining a pressurizing force control coefficient according to the power head torque and/or the power head rotating speed and controlling the pressurizing force according to the pressurizing force control coefficient.
9. The powerhead pressure control system of claim 8, wherein determining a pressure force control coefficient as a function of powerhead torque and/or powerhead rotational speed comprises:
determining a torque-pressure control coefficient and/or a rotation speed-pressure control coefficient;
and determining a pressurizing force control coefficient according to the torque-pressurizing force control coefficient and/or the rotating speed-pressurizing force control coefficient.
10. The powerhead pressurization control system of claim 9, wherein determining a pressurization control coefficient as a function of the torque-pressurization control coefficient and/or the speed-pressurization control coefficient comprises:
taking the torque-pressure control coefficient or the rotation speed-pressure control coefficient as the pressure control coefficient; alternatively, the result of the integrated calculation of the torque-applied pressure control coefficient and the rotation speed-applied pressure control coefficient is taken as the applied pressure control coefficient.
11. A rotary drilling rig comprising the power head pressure control system of any one of claims 8-10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110367649.7A CN113153136A (en) | 2021-04-06 | 2021-04-06 | Power head pressurizing force control method and system and rotary drilling rig |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110367649.7A CN113153136A (en) | 2021-04-06 | 2021-04-06 | Power head pressurizing force control method and system and rotary drilling rig |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113153136A true CN113153136A (en) | 2021-07-23 |
Family
ID=76888799
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110367649.7A Pending CN113153136A (en) | 2021-04-06 | 2021-04-06 | Power head pressurizing force control method and system and rotary drilling rig |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113153136A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113090248A (en) * | 2019-12-23 | 2021-07-09 | 中联重科股份有限公司 | Control method and device of rotary drilling rig and rotary drilling rig |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101844510A (en) * | 2002-12-25 | 2010-09-29 | 丰田自动车株式会社 | Control unit for hybrid drive unit |
| CN202417468U (en) * | 2011-12-14 | 2012-09-05 | 北京市三一重机有限公司 | Rotary drilling jig and pressure and torque matching device thereof |
| CN203743101U (en) * | 2014-01-20 | 2014-07-30 | 龙工(上海)机械制造有限公司 | Multi-torque hydraulic system of power head of rotary drilling rig |
| CN105402039A (en) * | 2015-12-21 | 2016-03-16 | 徐州燕大传动与控制技术有限公司 | Power matching method based on torque and rotation speed compound control for rotary drilling rig |
| US20190345779A1 (en) * | 2017-01-27 | 2019-11-14 | Kobold Corporation | Coil tubing bottom hole assembly with real time data stream |
| CN110984956A (en) * | 2019-11-27 | 2020-04-10 | 上海中联重科桩工机械有限公司 | Power head anti-sticking drilling electric control system, control method thereof and rotary drilling rig |
-
2021
- 2021-04-06 CN CN202110367649.7A patent/CN113153136A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101844510A (en) * | 2002-12-25 | 2010-09-29 | 丰田自动车株式会社 | Control unit for hybrid drive unit |
| CN202417468U (en) * | 2011-12-14 | 2012-09-05 | 北京市三一重机有限公司 | Rotary drilling jig and pressure and torque matching device thereof |
| CN203743101U (en) * | 2014-01-20 | 2014-07-30 | 龙工(上海)机械制造有限公司 | Multi-torque hydraulic system of power head of rotary drilling rig |
| CN105402039A (en) * | 2015-12-21 | 2016-03-16 | 徐州燕大传动与控制技术有限公司 | Power matching method based on torque and rotation speed compound control for rotary drilling rig |
| US20190345779A1 (en) * | 2017-01-27 | 2019-11-14 | Kobold Corporation | Coil tubing bottom hole assembly with real time data stream |
| CN110984956A (en) * | 2019-11-27 | 2020-04-10 | 上海中联重科桩工机械有限公司 | Power head anti-sticking drilling electric control system, control method thereof and rotary drilling rig |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113090248A (en) * | 2019-12-23 | 2021-07-09 | 中联重科股份有限公司 | Control method and device of rotary drilling rig and rotary drilling rig |
| CN113090248B (en) * | 2019-12-23 | 2023-03-14 | 中联重科股份有限公司 | Control method and device of rotary drilling rig and rotary drilling rig |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2518220B1 (en) | Apparatus and method for controlling a hydraulic pump of a construction machine | |
| EP2518222B1 (en) | Power control apparatus for a construction machine | |
| CN103470485A (en) | Variable pump power control method, equipment and system and concrete pumping device | |
| US6314727B1 (en) | Method and apparatus for controlling an electro-hydraulic fluid system | |
| CN104934943A (en) | Overvoltage protection device, overvoltage protection method and electrolytic-capacitor-free motor driving system | |
| EP2610492B1 (en) | Motor control unit and electric pump unit | |
| JP2012082643A5 (en) | ||
| CN101818506B (en) | Limit load regulating method of static pressure driving bulldozer using electronic control motor | |
| CN113153136A (en) | Power head pressurizing force control method and system and rotary drilling rig | |
| JP2017512933A (en) | Electronic torque and pressure control for load sensing pumps | |
| JP5585487B2 (en) | Power source device for hybrid construction machinery | |
| JP2017022948A (en) | Actuator control device and actuator unit | |
| WO2011057606A2 (en) | Compressor for producing compressed air | |
| EP2294319B1 (en) | Hydraulic device control | |
| CN102418689B (en) | Variable pump control system and method, hydraulic walking equipment and control method thereof | |
| US20160363117A1 (en) | Electronic torque and pressure control for load sensing pumps | |
| KR20120130654A (en) | Method for controlling output of motor driven power steering system | |
| JP5218152B2 (en) | Control device for electric vehicle | |
| US20150184680A1 (en) | Torque Limit Control | |
| JP6231630B1 (en) | Vibration control device for railway vehicles | |
| WO2019171911A1 (en) | Railroad car vibration damping device | |
| KR101631718B1 (en) | Apparatus and method for controlling engine torque automatically by fan load in construction equipment | |
| KR100468491B1 (en) | Method for preventing overheat of motor in electric power steering system | |
| US10427687B2 (en) | Speed ratio based governor selection | |
| KR101154675B1 (en) | Velocity control apparatus and method for the cooling fan of heavy machinery |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20210723 |
|
| RJ01 | Rejection of invention patent application after publication |