Patent Application
20100124509
This invention relates to reciprocating compressors for transporting natural gas, and more particularly to a method for reducing pulsations in the compressor system associated with such compressors.
To transport natural gas from production sites to consumers, pipeline operators install large compressors at transport stations along the pipelines. Natural gas pipeline networks connect production operations with local distribution companies through thousands of miles of gas transmission lines. Typically, reciprocating gas compressors are used as the prime mover for pipeline transport operations because of the relatively high pressure ratio required. Reciprocating gas compressors may also be used to compress gas for storage applications or in processing plant applications prior to transport.
Reciprocating gas compressors are a type of compressor that compresses gas using a piston in a cylinder connected to a crankshaft. The crankshaft may be driven by an electric motor or a combustion engine. A suction valve in the compressor cylinder receives input gas, which is then compressed by the piston and discharged through a discharge valve.
Reciprocating gas compressors inherently generate transient pulsating flows because of the piston motion and alternating valve motion. Various devices and control methods have been developed to control these pulsations. An ideal pulsation control design reduces system pulsations to acceptable levels without compromising compressor performance.
A more complete understanding of the present embodiments and advantages thereof may be acquired by referring to the following description taken in conjunction with the accompanying drawings, in which like reference numbers indicate like features, and wherein:
The following description is directed to using a frequency modulation method to continuously vary the piston speed of a reciprocating compressor. This avoids the creation of coherent wave resonance in the compressor piping system.
In the example of
The following description is written in terms of the “generic” compressor system 100. However, the same concepts are applicable to other compressor configurations.
A typical application of compressor system 100 is in the gas transmission industry. The compressor system operates as a “station” between two gas transmission lines. The first line, at an initial pressure, is referred to as the suction line. The second line, at the exit pressure for the station, is referred to as the discharge line. The suction and discharge lines are also referred to in the industry as the “lateral piping”. The pressure ratio (discharge pressure divided by suction pressure) may vary between 1.25-4.0, depending on the pipeline operation requirements and the application.
Filter bottles 18a and 18b may be used to reduce compressor system pulsations. These filter bottles are placed between the compressor and the lateral piping, on the suction or discharge side or on both sides. The effectiveness of filters of this type is dependent on the pulsation frequencies that need to be controlled due to the speed of the compressor.
Controller 17 is used for control of parameters affecting compressor load and capacity. The pipeline operation will vary based on the flow rate demands and pressure variations. The compressor must be capable of changing its flow capacity and load according to the pipeline operation. As explained below, the controller includes control circuitry and programming for controlling the engine speed. Continuous shifting of the compressor operating speed inhibits the creation of standing waves in the piping, which avoids amplification of piping system resonances.
Controller 17 is equipped with processing and memory devices, appropriate input and output devices, and an appropriate user interface. It is programmed to perform the various control tasks and deliver control parameters to the compressor system. Given appropriate input data, output specifications, and control objectives described herein, algorithms for programming controller 17 may be developed and executed.
Compressor 12 is operated at a speed that is dictated by the pressure and flow requirements of the gas transmission pipeline. As long as suction and discharge pressure and flow conditions remain the same, the compressor speed need not change.
As explained below, the “compressor speed” for purposes of the present invention is an “average compressor speed” as a result of frequency modulation about a given operating speed. In contrast, in a conventional compressor system, the compressor speed is “fixed”. Most modern compressors are capable of operating over a range of speeds so that they can adjust to the demands of the pipeline. However, in conventional compressor operation, the fixed compressor speed changes only two or three times per day (at most) because pipeline operating demands tend to be quite stable.
A feature of the invention is the focus on the excitation source for pulsation avoidance. To create pipeline pulsations, two components are necessary: a pulsation excitation source and an acoustic pipe response of a matching wavelength. If the frequency of the compressor's piston-valve pressure pulsations coincides with an acoustic length of an upstream or downstream pipe, an acoustic resonance condition exists.
As stated in the Background, the result of the resonance condition is pressure pulsations that can damage the compressor system or its piping. Filter bottles 18a and 18b are an example of conventional technology that seeks to induce a pressure loss and thereby affect the wave shape. Examples of other conventional pulsation control techniques include special orifice and choke tube designs.
250 Hp Driver
Pressure ratio 2.0
Operating speed=500-900 RPM
Typical natural gas working fluid
A pulsation prediction tool for the above compressor case was used to obtain the response of
More specifically, control unit 17 is programmed to control the engine speed to modulate the excitation frequency about a given operating (average) engine speed. In other words, the method relies on modulation of the excitation frequency of the compressor such that, although the compressor never operates at a single frequency, the compressor's average operating speed results in the required average compression and flow performance. This is accomplished by continuously and randomly varying the running speed of the compressor about the desired operating point within a prescribed range.
The speed ramp rate and range (both increasing and decreasing) of the compressor may be probabilistically determined. The overall statistical distribution is such that it minimizes the formation of coherent waves in the piping system while still maintaining the compressor's desired performance over a reasonable time period.
Control unit 17 may be programmed with any one of various algorithms and statistical distributions. The programming controls the compressor speed by controlling both the ramp rate and range. The optimal selection of the specific control method depends on the specific resonances that are to be avoided and the mechanical limitations of the compressor and driver (engine or motor). The control method can be implemented through a variety of electrical, mechanical or hydraulic means, such as a controlled variable frequency drive (for electric motor drives) or variable speed gears (for gas engine drivers).
Control unit 17 may be programmed to automatically perform at least the process of determining the driver speed modulation characteristics and the delivery of control signals to the driver. Data representing the desired operating speed for given system flow and pressure, as well as the frequency response(s) to be avoided, may be input from other sources, or may also be determined by appropriate programming of the control unit or associated processing devices.
Step 51 is determining a desired operating speed for the driver. This determination is typically primarily based on desired pipeline flow and pressure parameters.
Step 52 is determining the pulsation response of the system at that operating speed. This may be accomplished by direct feedback from sensors associated with the system, such as by one or more dynamic pressure sensors in the piping and/or vibration sensors on the piping. Alternatively, the pulsation response may be estimated from historic data from past system responses. As a third alternative, the pulsation response data may be obtained from a compressor system modeling and pulsation prediction tool, such as that used to obtain the data of
Step 53 is determining the modulation characteristics for modulating the operating speed in a manner that will result in an equivalent average operating speed and that will minimize any resonant response(s) of the system. As explained above, this determination uses probabilistic techniques to determine a random modulation. Various algorithms may be used to receive input data, such as data representing the desired average operating speed and the resonant response, and to determine continuously varying speeds and rates of change that will minimize the pulsation response of the compressor system.
Step 55 is using the modulation data to vary the speed of the compressor driver. As explained above, this results in reduced system pulsations.
Step 55 is performed by control unit 17, and the extent to which the other above steps are performed by control unit 17 is a design choice. For example, the desired operating speed and the pulsation response may be determined from other sources or by additional programming of the control unit 17. Similarly, the modulation characteristics could be algorithmically determined in real time by control unit 17 or could be accessed from stored data. For purposes of this description, a “determination” of data by control unit 17 is to be interpreted broadly and could include for example, receiving data from sensors or another processing unit, accessing the data from memory, or by on-board calculation.
