MXPA06008973A - Safemode operating system for a drilling or service rig - Google Patents

Abstract

Disclosed herein is a system designed to manage or slow the block travel speed down to safe speeds when the rig is operating in a light load/high speed condition. The system monitors and controls engine torque and horsepower, providing the minimum amount of each necessary to pull the light load out of the hold without providing sufficient excess torque to pull the load through a snag.

Description

SAFE MODE OPERATING SYSTEM FOR A PERFORATION OR SERVICE EQUIPMENT BACKGROUND OF THE INVENTION This application is based on the Provisional Application of E.U.A. Serial No. 60 / 548,838, entitled "Safe Mode Operation System for an Oil Well Equipment" by Fred M. Newman, filed on February 27, 2004, incorporated by reference in its entirety herein. Through the history of oil well drilling and service, accidents, some still involving fatalities, frequently occur when a team is pulling tubulars and running the tubulars toward a well head, BOP, wedges, or other stationary appliances. Normally, when the equipment is pulling shallow and has light load, the block speed is fast and there is little time to react to unexpected occurrences. Compounding the speed problem, there is no space or stretching in the pipe or drill pipe, and in this way, when the pipe hangs up, damage and accidents frequently occur. When a team starts to pull tubulars out of a borehole, the operator or driller will select the most efficient gear to pull the load based on the weight of the hook load and the desired speed of the traction. More often than not, the operator pulls as fast as possible, however, the block pull speed is limited to both the main mover (engine) power and the gear train that transfers the power from the engine to the crane. . Since the hook loads coming out of the bottom of a hole can be raised, normal equipment with the normal operator will start pulling out of the bottom by pulling slowly (motor driven to full but still slow block movement) and as the load Hook decreases with less pipe in the bore, the traction speed or block speed will increase. This is mainly due to the requirement of reduced power to lift the lighter load. The drill pipe, pipe and rods all have a known modulus of elasticity and exhibit the ability to stretch. For example, if a computer has 3,048 meters (10,000 feet) of measured surface pipe that weighs 20,412 kg (45,000 pounds), and the pipeline is not moving, the weight indicators will perceive 20,412 kg. (45,000 pounds as long as the pipe is free hanging and vertical.) The bottom of the pipeline will be approximately 3,048.91 meters (10,003 feet) due to normal stretch when free hanging.When subjected to forces in excess of the weight of free hanging, such as such being stuck in the well where the bottom of the tube is stationary and the top of the tube is being pulled by the block is moving, the tubular string will be lengthened.The amount of additional stretching can be defined by the following equation: ) stretched (inch) - [Pozol tube length ""! * [Traction Difference [735, 000] * [Tube weight] When a tubular is sunk deep in a well, the operator reaction time is significantly longer than when a tubular sinks near the surface. For example, if a tubular of 60.32 mm (2-3 / 8") to 2.041 kg (4.5 pounds) by 30.48 cm (foot) sinks to 3,048 (10,000 feet) and the free hanging weight is 20,412 kg (45,000 pounds). The maximum desired traction would then be 29,484 kg (65,000 pounds), which is based on a calculated value based on the 90% relaxation point of new pipeline.The equipment operator pulls an additional 20,000 pounds on the weight of hanging free (ie the maximum of 29,484 kg (65,000 pounds), the total stretch in the pipe would be: 2) S = [3,048 m (10,000 feet) * 9,0972 kg (20,000 pounds) of traction] / 333, 396 * 1.372 kg / (735, 000 * 4.5 # / ft)] = 152.4 cm (60 inches) Using this equation and applying it to equipment that pulls out of the well, a determination can be made to what the operator sees when the pipe sticks while pulling, assuming that the machine's pulling speed is, at that depth and weight, about 18,288 m (60 feet) per minute or 20.48 cm (1 foot) per second), and knowing from equation 2 that a traction of 9,072 kg (20,000 pounds) on traction provides a stretch of 152.4 cm (60 inches), the time taken from the adhesion to a stretch of 9,072 kg (20,000 pounds) of stretching, the time taken from adhesion to a 9,072 kg (20,000 lb) pull can be calculated as follows : 3) T = D / V Where D is the distance pulled, V = speed and T is time. Being that at a traction of 9,072 kg (20,000 pounds) The tubular is stretched 152.4 cm (60 inches), or 1,524 m (5 feet) and the speed at that depth is 30.40 cm (1 foot) per second, the time can be calculated as follows: 4) T = 5 / lo or five seconds In other words, if the pipe adheres near the bottom of the well, the operator has about 5 seconds to react and stop the blocks before reaching the maximum allowable tension of 29,484 kg (65,000 pounds), ie , a traction of 9,072 kg (20,000 pounds). Of course, the higher the speed, the less reaction time is provided to the operator, however, the traction is usually observed quickly by the operator, and therefore, the operator usually has time to stop the equipment and take evasive action to Avoid over traction. Comparing the example of deep well adhesion with an example of shallow adhesion the example amplifies the problem facing the drilling and well service industry. Assume that the tubular itself is at a depth of only 152.4 m (500 ft), the tubular has a hanging weight of 1,020.60 kg (2,250 lb), the same 2.0412 kg (4.5 lb) per 30.48 cm (1 ft). Now, the equipment operator has more than enough power to pull at almost any speed, but still does not want to pull more than 29,484 kg (65,000 pounds), which in this case is an over traction of 48,463.40 kg (62,750 pounds). Using Equation 1, the tubular stretch in this example is calculated as follows: 5) 5 = [152.4 m (500 feet) * 48,463.40 kg (62,750 pounds) of traction / [333, 396 * 1,372 m (735,000 * 4.5 # / foot] = 22.86 c (9 inches) Assuming that the traction speed for a light load is fast at 1,219 m (4 feet) per second, using equation 3 the time for this example "almost out of the hole" can be calculated as follows: 6) T = .15 / = .1875 seconds to react. As shown, the time to travel 22.86 mm (9 inches), that is, to stretch the hanging weight to maximum traction 7.62 cm (1/4 foot), to 1,219 m (4 feet) per second is .1875 seconds , significantly slower when the tubular sinks deep into the well. Even when the equipment is operated at a much smaller gear and the speed becomes slow at 30.48 cm (1 foot) per second, using equation 3 again to calculate the time, it can be shown that there is still not enough time (3/4 one second) to react appropriately to a shallow adhesion situation: 7) T = .75 / 1 = second to react As shown, when the equipment has well problems that cause adhesion, if there is a long tube length in the well, the operator has a sufficient amount of time to react. If, on the other hand, the length of the tube is short and the equipment is operating at maximum capacity, there is little or no time to react and the probabilities of a catastrophic event greatly increase. It remains, therefore, important to find a solution to this problem to provide the team and crew with an extra level of security to prevent these catastrophes.

SUMMARY OF THE INVENTION A system designed to handle or slow down the block travel speed downward at safe speeds when the equipment is operating in a light load / high speed condition is described herein. The system monitors and controls the torque and engine power, providing the minimum amount of each necessary to pull the light load out of the well without providing enough excess torque to pull the load through an obstacle. The system can be activated manually, or it can be activated automatically when the hook load drops below some predetermined value. When in operation, the system adjusts a maximum engine RPM to pull the well load, and warns the operator as to the highest gear available to pull the load. The system activates a transmission-mounted solenoid that releases the pressure from the clamping clutch cylinder line, keeping the system in a sliding mode and out of the holding mode. The system also activates a particularity of DTL (Digital Torque Limitation) of the engine, limiting the power output of the engine. Finally, the system can also limit the air pressure of the clutch blister on the pipe crane to keep the system operating in the safe mode. This system is applicable to all equipment used in the field, including, but not limited to, drilling equipment and well service equipment. DESCRIPTION OF ILLUSTRATIVE MODALITIES One embodiment of the present invention limits the available power to the engine while pulling a light load. A rig that pulls a pipe or drill string needs some calculable amount of power to pull both the hook load and activate the pliers to unscrew the pipe. More power is obviously required to pull 1,524 meters (5,000 feet) of pipe than to pull 152.40 m (500 feet) of pipe at the same speed. The majority of the equipment that currently works in the field has 400 HP deliverables to the crane. This is optimal when pulling pipe from deep into the well, but it can be dangerous when working shallow, since having too much power when an unexpected event occurs can lead to stress on the equipment and a possible accident. A generic equipment that pulls 304.8 m pipe (1,000 feet) uses less than 550 foot-pounds or torque. The same equipment, pulling 15240 m (5000 ft) of pipe use 2,500 foot-pounds or torque. The traction speed dictates the actual power that is being used by the motor. It would seem that when the equipment is shallow and only needs the 550 foot-pounds of torque, the excess torque is not used in the pulling task, but instead is available for over-pulling and over-stretching. tubular. Therefore, limiting the power supplied to activate the crane to only the necessary amount of torque needed to pull the pipe would add a level of safety to the equipment crew. So, for example, if a packer hangs at the wellhead, the motor and torque convert will clog before the pipe is over-tensioned. Limit torque can be achieved in modern engines (series 60 or other brands of type EDC) by reversing a switch that reconfigures the fuel map. This process is called "DTL" which is an acronym for "Digital Torque Limitation." To the computer responsible for engine control, DTL does no more than change the flow of fuel to the engine when it is commanded to do so. The motor in normal mode will inject an appropriate amount of fuel into the engine to obtain a desired RPM In the DTL mode, the fuel flow to the engine is reduced, resulting in the engine getting the desired RPM, but at a Reduced torque output Starting the DTL when the hook load falls below a specified minimum can provide some protection to the team and crew components while preventing a catastrophic event.An additional embodiment of the present invention includes limiting the drum clutch air pressure The pipe drum clutch is the mechanical link between the rotating components of the drive train and the crane. Drum air clutch is activated by air pressure in excess of 7.03 kg / cm2 (100 psi). Since the engine clutch is normally a friction type clutch, the total applied force is always at its maximum, which minimizes clutch slippage. Minimizing clutch slippage is desirable when pulling heavy loads. When the loads are light, however, the problem of "heavy load" clutch slip is no longer a problem. In fact, if a tubular is sunk in the well, the lack of slippage becomes problematic, instead of being beneficial. To allow such clutch sliding during light load operations, a second air line feeding the clutch can be installed. The main line, currently in use on all equipment, would be used to supply full air to the clutch ampule and would be used when pulling heavy loads. The second path or line, activated by a simple solenoid valve, once the hook load falls below a specified minimum value, runs through a pressure regulator before feeding the clutch ampule. If the pressure output of the regulator was limited, for example, to 2,812 kg / cm2 (40 psi), the clutch would slip when the hook load exceeds 18,144 kg (40,000 pounds), adding an additional level of safety in the event that tubulars were unexpectedly retained above. A further embodiment of the present invention includes introducing slippage in the torque converter. The engine provides power to the crane through a torque converter, a transmission, and then a gear train that drives the chains and finally the crane. When the equipment is lifting heavy loads, the engine chokes and spins a turbine pump. The fluid energy of this turbine pump is transferred through the stator to a turbine wheel, the turbine wheel then rotates the turbine shaft which in turn drives a gear reduction train that finally drives the output shaft that transfers the motor power to the crane. The engine starts at idle speed and then accumulates RPM, putting more energy to the turbine through the pump. Initially there is a large amount of slip between the pump and the turbine, but as the output turbine shaft gains speed and the engine reaches a high RPM, there is less need for this slippage. As the engine reaches a high RPM, the turbine pump or Pitot tube sensor senses high pressure due to high engine RPM and then transfers fluid to a piston concentric to the turbine shaft that activates the clutch clutch. With the clamping clutch activated, the motor is now directly coupled to the turbine shaft that drives the non-slip transmission and the gear train. When the transmission is in hold, the torque converter (slip supplier) is out of circuit, resulting in a direct mechanical coupling between the 400 HP motor and the crane without slip, handling the torque converter and Keeping the system out of the way during light load events can help a team to ensure slippage, thus adding another level of safety when pulling the last part of the pipe out of the well. During normal equipment operations, that is, when working under heavy loads, the fluid from the motor-driven turbine pump activates the clamping system that runs at approximately 6,327 kg / cm2 (90 psi). When the pump fluid pressure reaches some set value, the fluid applies pressure to the clamping clutch pressure plates and, as long as the plates are under pressure, the clamp is engaged. There is a discharge port in the outer housing of the transmission that is usually marked as "front regulator pressure". Placing a normally closed solenoid valve in this port and activating this valve when slipping is needed (ie, pulling light loads) allows the clamping fluid pressure to return to the fluid reservoir, keeping the torque converter out of the way . If the valve is not activated, the drive converter and torque behave normally and go to clamping when needed. While the apparatuses and methods of this invention have been described in terms of preferred embodiments, it will be apparent to those skilled in the art that variations to the process described herein may be applied without departing from the concept and scope of the invention. All substitutes and similar modifications apparent to those skilled in the art are considered to be within the scope and concept of the invention as set forth in the following claims,

Claims (18)

1. CLAIMS 1.- A method to prevent a catastrophic event of light load on an oil rig that includes: specifying a minimum hook load weight, supervising the torque needed to pull tubulars from a bed once the load weight of hook falls below the specified minimum hook load weight.
2. 2. The method according to claim 1, wherein the motor power is limited using a digital torque limitation process.
3. 3. The method according to claim 1, wherein the weight monitoring steps of hook load and motor power limitation are manually made.
4. 4. The method according to claim 1, wherein the steps of supervising weight of hook load and limitation of motor power are made automatically.
5. 5. - The method according to claim 1, wherein the engine power limitation step is achieved by reducing the flow of fuel to the engine.
6. 6. The method according to claim 1, wherein the oil equipment is a drilling rig or a well service team.
7. 7. - A method to prevent a catastrophic light load event in an oil rig comprising: specifying a minimum weight of hook load monitoring the hook load weight, reducing the pressure applied to the engine clutch ampule once that the hook load weight falls below the specified minimum hook load weight.
8. 8. The method according to claim 7, wherein the steps of monitoring the weight of hook load and reducing pressure of the motor clutch blister are done manually.
9. 9. The method according to claim 7, wherein the steps of monitoring the hook load weight and limiting the motor power are made automatically.
10. 10.- The method. according to claim 7, wherein the oil rig is a drilling rig or a well service rig.
11. 11.- A method to prevent a catastrophic event of light load in a petroleum equipment that includes: specify a minimum hook load weight, supervise the weight of hook load, introduce slip to the torque converter of oil equipment once the hook load weight falls below the specified minimum hook load weight.
12. 12. The method according to claim 11, wherein slip is introduced to the torque converter keeping the torque converter out of clamping mode.
13. 13. The method according to claim 12, wherein the torque converter is kept out of clamping mode by releasing the fluid pressure of the turbine pump driven by oil equipment engine.
14. 14. The method according to claim 11, wherein the steps of supervising hook load weight and introducing slip in the torque converter of petroleum equipment are done manually.
15. 15. The method according to claim 11, wherein the steps of monitoring the weight of hook load and introducing slip in the torque converter of oil equipment are done automatically.
16. 16. - The method according to claim 11, wherein the oil equipment is a drilling rig or a well service equipment.
17. 17.- A method to prevent a catastrophic light load event in an oil rig that includes: specifying a minimum hook load weight, monitoring the engine power supplied to activate the oil rig crane to only the necessary amount of torque required to pull tubulars from a well once the hook load weight falls below the specified minimum hook load weight, reduce the pressure applied to the drum clutch ampule once the load weight of hook falls below the specified minimum hook load weight, and slip into the oil equipment torque converter once the hook load weight falls below the specified minimum hook load weight.
18. 18. The method according to claim 17, wherein the oil rig is a drilling rig or a well service rig.