US20130115042A1

US20130115042A1 - Dynamic thrust balancing for centrifugal compressors

Info

Publication number: US20130115042A1
Application number: US13/518,574
Authority: US
Inventors: Gabriele Mariotti; Claudia Cagnarini
Original assignee: Nuovo Pignone SpA
Current assignee: Nuovo Pignone SpA
Priority date: 2009-12-22
Filing date: 2010-12-16
Publication date: 2013-05-09
Also published as: AU2010335267A1; EP2516866A2; MX2012007457A; RU2012127256A; CN102762871A; ITCO20090072A1; CN102762871B; CA2785334A1; IT1397707B1; WO2011076668A2; WO2011076668A3; BR112012015363A2; RU2557143C2; KR20120123351A; JP5928827B2; JP2013515192A

Abstract

Systems and methods for dynamically balancing axial loads in centrifugal compressors to reduce residual axial loads on the bearings used therein are described. A sensor or probe detects a parameter associated with the axial load acting on the bearing. Based on the detected parameter, the pressure in a balance chamber is controlled to adjust the compensating axial force generated by a balance drum.

Description

CROSS REFERENCE TO RELATED APPLICATIONS

This is a national stage application under 35 U.S.C. §371(c) of prior-filed, co-pending PCT patent application serial number PCT/EP2010/070001, filed on Dec. 16, 2010, which claims priority to Italian Patent Application Serial No. CO2009A000072, filed on Dec. 22, 2009, the entire contents of which are incorporated herein by reference.

BACKGROUND OF THE INVENTION

The present invention relates generally to centrifugal compressors and, more specifically, to balancing thrust in such compressors.
A compressor is a machine which increases the pressure of a compressible fluid, e.g., a gas, through the use of mechanical energy. Compressors are used in a number of different applications, including operating as an initial stage of a gas turbine engine. Gas turbine engines, in turn, are themselves used in a large number of industrial processes, including power generation, natural gas liquification and other processes. Among the various types of compressors used in such processes and process plants are the so-called centrifugal compressors, in which the mechanical energy operates on gas input to the compressor by way of centrifugal acceleration which accelerates the gas particles, e.g., by rotating a centrifugal impeller or rotor through which the gas passes.
Centrifugal compressors can be fitted with a single rotor, i.e., a single stage configuration, or with a plurality of rotors in series, in which case they are frequently referred to as multistage compressors. Each of the stages of a centrifugal compressor typically includes an inlet conduit for gas to be compressed, a rotor which is capable of providing kinetic energy to the input gas and an exit pipe which converts the kinetic energy of the gas leaving the rotor into pressure energy.
Multistage centrifugal compressors are subjected to an axial thrust on the rotor caused by the differential pressure across the stages and the change of momentum of the gas turning from the horizontal to the vertical direction. This axial thrust is normally compensated by a balance piston and an axial thrust bearing. Since the axial thrust bearing cannot be loaded by the entire thrust of the rotor, a balance piston is designed to compensate for most of the thrust, leaving the bearing to handle any remaining, residual thrust. The balance piston is normally implemented as a rotating disc or drum which is fitted onto the compressor shaft, such that each side of the balance disc or drum is subjected to different pressures during operation. The diameter of the balance piston is chosen to have a desired axial load to avoid its residual load from overloading the axial bearing. Conventional oil-lubricated bearings are typically designed to withstand axial thrust forces on the order of four times the maximum residual axial thrust which are expected to occur during abnormal, e.g., surging, conditions.
However, when the gas conditions change during operation in the compressor, the compensation provided by the balance piston may not be sufficient to avoid bearing overload. Indeed some types of centrifugal compressors are more likely than others to experience such gas condition variations, e.g., in gas storage applications for multistage centrifugal compressors employing parallel operation, wherein the difference in axial thrust between the first and second sections of the compressor, linked to flow coefficient difference, may not be readily compensated for by the balance piston. Thus, conventional oil-lubricated bearings are typically designed to withstand axial thrust forces on the order of four times the maximum residual axial thrust which are expected to occur during abnormal, e.g., surging, conditions.
Another recent development involves substituting active magnetic bearings (AMBs) for conventional oil-lubricated bearings as the axial (and radial) rotatable support for the compressor shaft. AMBs operate by based on electromagnetic principles to control axial and radial displacements within the compressor. Briefly, AMBs include an electromagnet driven by a power amplifier which regulates the voltage (and therefore the current) into the coils of the electromagnet as a function of a feedback signal which indicates displacement of the compressor's rotor inside the device. AMBs have the desirable attribute that they do not require oil as a lubricant, reducing overall maintenance of the compressor system and, potentially, removing the requirement to provide seals between the impellers and the bearing. However AMBs also have the drawback that they are not capable of handling as much axial thrust as the conventional oil-lubricated bearings.
Accordingly, it would be desirable to design and provide methods and systems for dynamic thrust balancing in such compressors which overcome the aforementioned drawbacks of existing balancing systems.

BRIEF DESCRIPTION OF THE INVENTION

Exemplary embodiments relate to systems and methods for dynamically balancing axial loads in centrifugal compressors to reduce residual axial loads on the bearings used therein. A sensor or probe detects a parameter associated with the axial load acting on the bearing. Based on the detected parameter, the pressure in a balance chamber is controlled to adjust the compensating axial force generated by a balance drum. This results in a reduction in the residual axial forces acting on the bearings across different operating conditions. However, it will be appreciated by those skilled in the art that such advantages are not to be construed as limitations of the present invention except to the extent that they are explicitly recited in one or more of the appended claims.
According to an exemplary embodiment, a centrifugal compressor includes a rotor assembly including at least one impeller, a bearing connected to, and for rotatably supporting, the rotor assembly, a stator, a balance drum disposed between said at least one impeller and said bearing, a balance chamber, defined at least in part by an outboard side of said balance drum, and having a balance line connected thereto, a sensor for sensing a parameter which is associated with an axial load on said bearing, and a control valve for varying a pressure within the balance chamber based on the sensed parameter.
According to another exemplary embodiment, a method for dynamically balancing axial load acting on a bearing in a centrifugal compressor includes the steps of detecting a parameter associated with the axial load, and controlling a pressure in a balance chamber proximate a balance drum in the centrifugal compressor based on the detected parameter to dynamically balance the axial load acting on the bearing.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings illustrate exemplary embodiments, wherein:

FIG. 1 is a schematic view of a multistage-type centrifugal compressor, which can be provided with dynamic balancing mechanisms according to exemplary embodiments;

FIG. 2 depicts static axial load balancing in a centrifugal compressor;

FIG. 3 depicts dynamic axial load balancing in a centrifugal compressor according to an exemplary embodiment; and

FIG. 4 is a flowchart illustrating a method for dynamic load balancing according to an exemplary embodiment.

DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION

The following detailed description of the exemplary embodiments refers to the accompanying drawings. The same reference numbers in different drawings identify the same or similar elements. Also, the following detailed description does not limit the invention. Instead, the scope of the invention is defined by the appended claims.
To provide some context for the subsequent discussion relating to thrust balancing systems according to these exemplary embodiments, FIG. 1 schematically illustrates a multistage, centrifugal compressor 10 in which such thrust balancing systems may be employed. Therein, the compressor 10 includes a box or housing (stator) 12 within which is mounted a rotating compressor shaft 14 that is provided with a plurality of centrifugal impellers 16. The rotor assembly 18 includes the shaft 14 and impellers 16 and is supported radially and axially through bearings 20 which are disposed on either side of the rotor assembly 18.
The multistage centrifugal compressor operates to take an input process gas from duct inlet 22, to increase the process gas' pressure through operation of the rotor assembly 18, and to subsequently expel the process gas through outlet duct 24 at an output pressure which is higher than its input pressure. The process gas may, for example, be any one of carbon dioxide, hydrogen sulfide, butane, methane, ethane, propane, liquefied natural gas, or a combination thereof. Between the rotors 16 and the bearings 20, sealing systems 26 are provided to prevent the process gas from flowing to the bearings 20. The housing 12 is configured to cover both the bearings 20 and the sealing systems 26, to prevent the escape of gas from the centrifugal compressor 10. According to different exemplary embodiments of the present invention, the bearings 20 may be implemented as either oil-lubricated bearings or active magnetic bearings. If active magnetic bearings are used as bearings 20, then the sealing mechanisms 26 may be omitted.
The centrifugal compressor 10 also includes the afore-described balance piston (drum) 28 along with its corresponding labyrinth seal 30. A balance line 32 maintains the pressure in a balance chamber 34 on the outboard side of the balance drum at the same (or substantially the same) pressure as that of the process gas entering via the inlet duct 22. However, according to exemplary embodiments described below, this balance line 32 includes a control valve which can modulate the pressure in the balance chamber 34 based upon, for example, sensed axial loading on or near the bearing 20 as will be described below with respect to FIG. 3.
Initially, however, it will be useful to describe the interaction of the various elements shown in FIG. 1 as they relate to axial loading in general by discussing FIG. 2. Therein, the various axial loading forces associated with operation of the centrifugal compressor 10 are illustrated conceptually. As shown in FIG. 2, the impellers 16 place an axial load (force) on the bearings 20 in the direction of the inboard (low pressure) side of the compressor 10 due to, e.g., differences between stages, changes in gas momentum, etc.. Although not shown in FIG. 2, the motor which rotates the compressor shaft 18 will place a (substantially constant) axial load in the opposite direction, i.e., toward the outboard (high pressure) side of the centrifugal compressor 10. To counteract the remaining axial load of the impellers 16, the balancing drum 28 is designed to exert an axial force in the outboard direction, the magnitude of which is based on the expected axial load of the impellers minus that of the motor. This is accomplished by, for example, designing the system such that the pressure Pu of the process gas on the inboard side of the balancing drum 28 is greater than the pressure Pe on the outboard side of the balancing drum 28, and by selecting a balancing drum of an appropriate size (diameter) to generate the desired balancing force. The pressure imbalance is developed and maintained by providing the balance line 32 between the balance chamber 34 and the main suction line associated with inlet duct 22 such that the pressure in the balance chamber is substantially the same as that on the inboard side of the impellers 16.
Ideally, the axial thrust compensation provided by the balance drum 28 would substantially offset the axial load placed on the bearings 20 by the impellers 16, or at least offset such an axial load enough that any residual load is within the design specifications of the bearings 20. However, as described above, operational variances within such compressors and/or the use of AMBs as bearings 20 may cause the residual loading to exceed the design tolerances of the bearings 20 for axial loading. Consider, for example, the following Table 1 which illustrates results from an axial loading test for an exemplary six impeller centrifugal compressor 10 having a balance drum 28 with a diameter of 231 mm rotating at 17000 rpm. This test compressor was equipped with AMBs as the bearings 20 which were nominally rated for axial loading of between +/−9000 N.

TABLE 1

% Flow	Motor Axial	Stages Axial	Drum Axial	Residual
Rate	Load [N]	Load [N]	Load [N]	Load [N]

141	11055	−74644	49557	−14032
140	11055	−76773	51973	−13745
130	11055	−103554	82378	−10121
120	11055	−122331	104646	−6630
110	11055	−137399	123401	−2943
100	11055	−149200	138755	609
90	11055	−157029	150214	4241
80	11055	−161512	157971	7514
73	11055	−162875	161356	9536

From Table 1, it can be seen that for flow rates of 73%, 130%, 140% and 141% of the designed nominal flow rate, the residual axial load, i.e., the axial load placed on the AMBs 20 of the centrifugal compressor, exceeded the +/−9000 N rating of the bearings using the configuration shown in FIG. 2, i.e., with an uncontrolled balance line 32.

According to exemplary embodiments of the present invention, a control valve 40 is placed on the balance line 32 to enable an automated control of the pressure Pe which is exerted on the outboard side of the balancing drum 28 as shown in FIG. 3. Therein, the same reference numerals as used in FIGS. 1 and 2 refer to the same or similar components of a centrifugal compressor 10. The control valve 40 regulates the pressure in the balance chamber 34 to vary the reaction force generated by the balancing drum 28 as a function of, for example, the bearing 20's displacement or the axial load on the bearing 20 as measured by a sensor or probe 42.
The control valve 40 thus controls the value of the pressure Pe and, accordingly, the amount of compensatory axial load provided by the balancing drum 28. More specifically, by closing the control valve 40, the pressure Pe increases thereby reducing the amount of compensatory axial load provided by the balancing drum 28. Alternatively, by opening the control valve 40, the pressure Pe decreases thereby increasing the amount of axial load provided by the balancing drum 28. When the control valve 40 is completely open, the maximum amount of compensatory axial load is generated by the balancing drum 28. Since the amount of load provided by the balancing drum 28 is, according to exemplary embodiments, controllably variable, it may be desirable to design the balancing drum 28 such that its maximum compensatory axial load is larger than that provided by conventional static balancing drums (i.e., by providing a larger balancing drum 28 to the system) since it is possible in these exemplary embodiments to reduce the amount of compensation being provided by closing the control valve 40 as desired.
As mentioned above, the control valve 40 is controlled based on a feedback signal from probe or sensor 42 regarding the amount of axial loading that the bearing 20 is experiencing at a given time. Measurements can be made periodically by the probe or sensor 42 and reported back to control logic 44 which is connected to control valve 40 to implement any desired control algorithm to open and close the valve 40 as needed to adjust for operating changes which result in more (or less) residual loading of the bearings 20. An exemplary relationship between the sensed axial loading and the operation of control logic 44 to control the gas pressure using valve 40 is discussed below with respect to Table 2. Control logic 44 may be implanted as an ASIC, FPGA, computer, or other type of processor and may be implemented purely in hardware, purely in software or in some combination thereof. The sensor or probe 42 may be any of a number of different types. For example, if the bearing 20 is an AMB, an induction sensor or probe such as a linear potentiometric displacement transducer (LPDT) can be used to measure displacement of the bearing 20 due to axial loading. Alternatively, if the bearing 20 is an oil-lubricated type of bearing, an eddy current sensor or probe may be a more appropriate implementation of sensor or probe 42. Other types of sensors, e.g., piezoelectric or sensors which measure pressure at the oil film in the bearing, may be used as alternatives.
According to one exemplary embodiment, control logic 44 can include a proportional integral derivative (PID) controller which automatically, in a closed loop, changes the pressure in the balancing drum chamber 34 as a function of the measured thrust on the machine. For example, for AMBs the currents on the coils of the AMBs are representative of the thrust that is controlled by the system. In particular if the current in the thrust bearing coil of an AMB exceeds a given value (threshold), the control logic 44 can act on the valve 40 via a simple PID controller. According to exemplary embodiments, the control system can be designed with a bias (hysteresis value) to avoid any thrust valve hunting.
A test was performed to evaluate the arrangement according to exemplary embodiments illustrated in FIG. 3 and to determine its ability to better control the residual load on the bearings 20. The test used the same type of centrifugal compressor 10 which was evaluated above to generate the results in Table 1, i.e., a six impeller centrifugal compressor running at 17000 rpm, except that the balance drum 28 was increased in size to have a diameter of 247 mm to provide for a slightly greater maximum compensatory axial load capability in this dynamic balancing arrangement. The results of the test are shown below in Table 2.

TABLE 2

%	Motor	Stages	Inlet	Drum	Residual
Flow	Axial	Axial	Pressure	Axial	Load
Rate	Load [N]	Load [N]	[bar]	Load [N]	[N]

141	11055	−74644	60	63141	−448
140	11055	−76773	60	66470	752
130	11055	−103554	65	92105	−394
120	11055	−122331	69	109779	−1497
110	11055	−137399	72	125865	−479
100	11055	−149200	75	137265	−881
90	11055	−157029	77	146551	577
80	11055	−161512	79	150734	277
73	11055	−162875	80	152146	326

It can be seen in Table 2 that the pressure Pe in the balance chamber 34 varies for at least most of the different flow rates in the table under the control of valve 40. The control valve is controlled by the sensor or probe 42 and control logic 44 such that is closed more (lower Pe pressure) for higher flow rates and more open (higher Pe pressure) for lower flow rates. As can be seen in the residual load column, this has the effect of controlling the residual load on the bearing 20 to within a much narrower range than was possible without the dynamic controls according to the exemplary embodiments. In fact the values are now easily within the design specifications for axial load handling of the AMBs (+/−9000 N). Note that in this example the nominal pressure in the balance chamber (i.e., when the control valve 40 is completely open) for this test setup is 52 bar. Those skilled in the art will appreciate that the parameters used in the test setups associated with Tables 1 and 2 are in all respects purely illustrative.
It will thus be further appreciated that exemplary embodiments enable for centrifugal compressors to be outfitted with smaller thrust bearings, since the axial loading on such bearings can be better controlled. In addition, such compressors are expected to have higher availability by reducing the residual load on such bearings. A method for controlling residual axial loading in such compressor systems according to exemplary embodiments can be performed as illustrated in the flowchart of FIG. 4. Therein, at step 100, a parameter associated with the axial load on the bearing is detected. Then, at step 102, a pressure in the balance chamber proximate the balance drum in the centrifugal compressor is controlled based on the detected parameter to dynamically balance the axial load acting on the bearing.
The above-described exemplary embodiments are intended to be illustrative in all respects, rather than restrictive, of the present invention. Thus the present invention is capable of many variations in detailed implementation that can be derived from the description contained herein by a person skilled in the art. All such variations and modifications are considered to be within the scope and spirit of the present invention as defined by the following claims. No element, act, or instruction used in the description of the present application should be construed as critical or essential to the invention unless explicitly described as such. Also, as used herein, the article “a” is intended to include one or more items.

Claims

What is claimed is:

1. A centrifugal compressor comprising:

a rotor assembly including at least one impeller;

a bearing connected to, and for rotatably supporting, the rotor assembly;

a stator;

a balance drum disposed between said at least one impeller and said bearing;

a balance chamber, defined at least in part by an outboard side of said balance drum, and having a balance line connected thereto;

a sensor for sensing a parameter which is associated with an axial load on said bearing; and

a control valve for varying a pressure within said balance chamber based on said sensed parameter.

2. The centrifugal compressor of claim 1, further comprising:

control logic configured to receive an output of said sensor and to control said control valve according to a predetermined function.

3. The centrifugal compressor of claim 2, wherein said predetermined function operates to increase pressure in said balance chamber when said axial load on said bearing exceeds a predetermined value.

4. The centrifugal compressor of claim 1, wherein said bearing is an active magnetic bearing.

5. The centrifugal compressor of claim 1, wherein said bearing is an oil-lubricated bearing.

6. The centrifugal compressor of claim 1, wherein said sensed parameter is displacement of said bearing.

7. The centrifugal compressor of claim 1, wherein said sensed parameter is axial load on said bearing.

8. The centrifugal compressor of claim 1, wherein said sensor is an induction sensor.

9. The centrifugal compressor of claim 1, wherein said sensor is a piezoelectric sensor.

10. The centrifugal compressor of claim 1, wherein said sensor is an eddy current sensor.

11. A method for dynamically balancing axial load acting on a bearing in a centrifugal compressor, the method comprising:

detecting a parameter associated with said axial load; and

controlling a pressure in a balance chamber proximate a balance drum in said centrifugal compressor based on said detected parameter to dynamically balance said axial load acting on said bearing.

12. The method of claim 11, wherein said step of controlling further comprises:

opening or closing a valve connected to a balance line which controls said pressure in said balance chamber.

13. The method of claim 11, wherein said step of controlling operates to increase pressure in said balance chamber when said axial load on said bearing exceeds a predetermined value.

14. The method of claim 11, wherein said bearing is an active magnetic bearing.

15. The method of claim 11, wherein said bearing is an oil-lubricated bearing.