Variable diffuser drive system

Abstract

A system is provided and includes a compressor. The compressor further includes a diffuser frame, a gas or oil actuator and a drive system. The diffuser frame defines a first channel through which compressed fluids are flowable, a second channel intersecting the first channel and a third channel extending from the second channel. The gas or oil actuator includes a piston and a head integrally coupled to the piston. The head and the piston are disposable in the second and third channels, respectively. The piston is movable in forward or reverse directions through the third channel such that the head is movable through the second channel and into or out of the first channel, respectively. The drive system is at least partially disposable in the third channel and configured to drive forward and rearward movements of the piston.

Claims

1. A system comprising: a compressor further comprising: a diffuser frame defining a first channel through which compressed fluids are flowable, a second channel intersecting the first channel and a third channel extending from the second channel; a gas or oil actuator comprising a piston and a head integrally coupled to the piston, the head and the piston being disposable in the second and third channels, respectively, and the piston being movable in forward or reverse directions through the third channel such that the head is movable through the second channel and into or out of the first channel, respectively; and a drive system at least partially disposable in the third channel and configured to drive forward and rearward movements of the piston, wherein: the first and second channels are annular, the third channel is axial, plural in number and arranged at multiple, evenly distributed annular locations, and the head comprises an annular body.

2. The system according to claim 1, wherein the compressor is fluidly interposed between a cooler and a condenser.

3. The system according to claim 2, wherein the compressor is receptive of lubrication from a pump, including a pump outlet, and an oil sump of a lubrication system.

4. The system according to claim 3, wherein the drive system is characterized in that the third channel is fluidly communicative with at least one of: the cooler and the condenser; and the oil sump and the pump outlet.

5. The system according to claim 1, wherein the gas or oil actuator comprises multiple pistons.

6. The system according to claim 1, wherein the drive system is re-configurable during operations thereof.

7. The system according to claim 1, wherein the drive system comprises a motor disposable in the third channel.

8. The system according to claim 1, wherein the drive system comprises a position sensor disposed within the second channel, the position sensor configured to sense a position of the head; and a control element configured to control the drive system in accordance with a sensing of the position of the head by the position sensor.

9. A centrifugal compressor with variable diffusion, comprising: a centrifugal compressor impeller; a gas or oil actuator disposed downstream from the centrifugal compressor impeller and comprising a piston and a head integrally coupled to the piston; a diffuser frame in which the centrifugal compressor impeller is rotatably disposable, the diffuser frame defining: a first channel through which compressed fluids flow from the centrifugal compressor impeller, a second channel in which the head is disposable and which intersects with the first channel, and a third channel in which the piston is disposable and which extends from the second channel; and a drive system at least partially disposable in the third channel to drive movements of the piston toward and away from positions at which the head at least partially blocks the first channel, wherein: the first and second channels are annular, the third channel is axial, plural in number and arranged at multiple, evenly distributed annular locations, and the head comprises an annular body.

10. The centrifugal compressor according to claim 9, wherein the drive system is receptive of pressurized fluids.

11. The centrifugal compressor according to claim 9, wherein the gas or oil actuator comprises multiple pistons.

12. The centrifugal compressor according to claim 9, wherein the drive system is re-configurable during operations thereof.

13. The centrifugal compressor according to claim 9, wherein the drive system comprises a motor disposable in the third channel.

14. The centrifugal compressor according to claim 9, wherein the drive system comprises: a position sensor disposed in the second channel, the position sensor configured to sense a position of the head; and a control element configured to control the drive system in accordance with a sensing of the position of the head by the position sensor.

15. A method of operating a variable diffuser drive system of a centrifugal compressor including a diffuser frame that defines a first channel through which compressed fluids flow, a second channel in which a gas or oil actuator head is disposable and which intersects with the first channel and a plurality of third channels in which at least one gas or oil actuator piston, to which the head is integrally coupled, is disposable and which extend from the second channel, the method comprising: determining a load condition of the centrifugal compressor; and driving forward and reverse movements of the at least one piston in the third channel toward and away from positions at which the head at least partially blocks the first channel in accordance with the load condition.

16. The method according to claim 15, wherein the driving comprises driving the movements of the at least one piston in concert.

17. The method according to claim 15, wherein the driving comprises at least one of hydraulic driving and motorized driving.

18. The method according to claim 15, wherein the driving comprises re-configuring a drive system at least partially disposed in the third channel.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The subject matter, which is regarded as the disclosure, is particularly pointed out and distinctly claimed in the claims at the conclusion of the specification. The foregoing and other features and advantages of the disclosure are apparent from the following detailed description taken in conjunction with the accompanying drawings in which:

(2) FIG. 1 is a schematic diagram of a heat exchanger system in accordance with embodiments;

(3) FIG. 2 is a side cutaway view of a variable diffusion drive system of a centrifugal compressor in accordance with embodiments;

(4) FIG. 3 is a side cutaway view of a variable diffusion drive system of a centrifugal compressor in accordance with further embodiments;

(5) FIG. 4 is a side cutaway view of a variable diffusion drive system of a centrifugal compressor in accordance with alternative embodiments;

(6) FIG. 5 is a schematic axial view of a diffuser of a centrifugal compressor in accordance with embodiments;

(7) FIG. 6 is a schematic diagram of a control element of a variable diffuser drive system in accordance with embodiments; and

(8) FIG. 7 is a flow diagram illustrating a method of operating a variable diffusion drive system in accordance with embodiments.

(9) These and other advantages and features will become more apparent from the following description taken in conjunction with the drawings.

DETAILED DESCRIPTION

(10) As will be described below, a variable diffuser drive system is provided and configured to move a piston into different positions directly using high pressure refrigerant from a condenser, high pressure oil from an oil pump or linear motor actuation.

(11) With reference to FIG. 1, a heat exchanger system 10 is provided. The heat exchanger system 10 includes a compressor 11, an expansion valve 12, a condenser 13 fluidly interposed between the compressor 11 and the expansion valve 12 and an evaporator or cooler 14 fluidly interposed between the expansion valve 12 and the compressor 11. The compressor 11 is operable to compress a saturated vapor therein and to output a high-pressure and high-temperature superheated vapor toward the condenser 13. The condenser 13 causes the superheated vapor received from the compressor 11 to condense through thermal transfer with water, for example. The condenser 13 outputs the resulting condensed liquid toward the expansion valve 12 as a saturated liquid. The expansion valve 12 abruptly reduced a pressure of the saturated liquid and produces a relatively cold mixture. The liquid of this cold mixture is then evaporated in the cooler 14 through thermal interactions with warm air blown over the cooler 14 and the resulting saturated vapor is returned to the compressor 11.

(12) The compressor 11 may include or be provided as a centrifugal compressor that operates by compressing fluids as a result of a rotation of the compressor 11 about a longitudinal axis thereof. Such rotation can be supported by bearings at opposite ends of the compressor 11, which receive lubrication from a lubrication system 15. The lubrication system 15 includes an oil sump 150 and a pump 151, which pumps pressurized oil from the oil sump 150, through the bearings and back to the oil sump 150.

(13) With continued reference to FIG. 1 and with additional reference to FIGS. 2-5, the heat exchanger system 10 may also include a diffuser 16 at an outlet of the compressor 11 and upstream from the condenser 13. The diffuser 16 converts kinetic energy (i.e., high velocity) of the gas flowing through it into pressure by gradually slowing or diffusing the gas velocity. Diffusers can be vaneless, vaned or an alternating combination thereof.

(14) In greater detail, as shown in FIGS. 2-4, where the compressor 11 is a centrifugal compressor, for example, the compressor 11 includes a centrifugal compressor impeller 20 and a diffuser frame 30. The centrifugal compressor 20 is rotatably disposable within or adjacent to the diffuser frame 30. The diffuser frame 30 is formed to define a first channel 31 through which compressed fluids flow from the centrifugal compressor impeller 20, a second channel 32 and a third channel 33.

(15) As shown in FIG. 5, the first channel 31 is annular and extends about the longitudinal axis of the compressor 11 and outwardly in a radial direction from an outward-most extent of the centrifugal compressor impeller 20. The second channel 32 intersects with the first channel 31 and is similarly annular and extends about the longitudinal axis of the compressor 11. The second channel 32 also extends axially in an aft direction from a mid-point of the first channel 31. The third channel 33 is oriented axially and is provided as plural third channels 33 that each extend axially in the aft direction from an end of the second channel 32. The plural third channels 33 are distributed substantially evenly along the annularity of the second channel 32.

(16) With continued reference to FIGS. 2-4, the compressor 11 is provided with a variable diffuser drive system 100 that offers variable diffusion capability and includes a gas or oil actuator 40 as well as a drive system 50. The gas or oil actuator 40 is downstream from the centrifugal compressor impeller 20 and includes a head 41 and a piston 42 to which the head 41 is integrally coupled. The head 41 is movable within the second channel 32 and into and out of the first channel 31 to at least partially block a flow of fluids through the first channel 31. The piston 42 is disposable within the third channel 33 and is movable in forward and reverse directions. When the piston 42 moves in the forward direction, the piston 42 urges the head 41 forward and into a blocking condition with respect to the first channel 31. Conversely, when the piston 42 moves in the reverse direction, the piston 42 urges the head 41 to also move in the reverse direction and out of the blocking condition with respect to the first channel 31. The drive system 50 is at least partially disposable in the third channel 33 and is configured to drive movements of the piston 42 toward and away from positions at which the head 41 opens the first channel 31 (e.g., a diffuser full-open position) or at which the head 41 at least partially blocks the first channel 31 (e.g., a diffuser full-closed position).

(17) In accordance with embodiments, the head 41 is ring-shaped and includes an annular body 410 (see FIG. 5). The piston 42 may be provided as plural pistons 42 that are respectively disposable in corresponding ones of the third channels 33.

(18) With the configuration of the first, second and third channels 31, 32 and 33 and with the construction of the gas or oil actuator 40 and the drive system 50, the variable diffusion capability of the compressor 11 is such that the movement of the head 41 into the first channel 31 can be controlled in accordance with various conditions, such as, but not limited to, full-load and part-load conditions.

(19) In accordance with exemplary embodiments and, as shown in FIG. 2, the drive system 50 may be characterized in that the third channel 33 is fluidly communicative with at least one of the cooler 14 and the condenser 13 (see FIG. 1) and with the oil sump 150 and an outlet of the pump 151 (see FIG. 1). The drive system 50 therefore may include: a controllable valve element 51, first piping 52 between the controllable valve element 51 and a first hydraulic chamber 53 of the third channel 33, and second piping 54 between the controllable valve element 51 and a second hydraulic chamber 55 of the third channel 33. The drive system 50 may also include additional piping 56 between the controllable valve element 51 and the cooler 14 and the condenser 13 or between the controllable valve element 51 and the oil sump 150 and the outlet of the pump 151.

(20) In the case of the additional piping 56 extending between each of the controllable valve elements 51 and the cooler 14 and the condenser 13, the controllable valve elements 51 may be operable such that the diffuser full-open and the diffuser full-closed positions are achievable.

(21) For example, at 75%/100% load capacity conditions, the controllable valve elements 51 can be operated or configured such that the first hydraulic chambers 53 are fluidly communicative with the condenser 13 and the second hydraulic chambers 55 are fluidly communicative with the cooler 14. This arrangement causes the pistons 42 to move in the reverse or rearward direction and thus urges the head 41 to retract in the reverse or rearward direction from the first channel 31 toward the diffuser full-open position. Meanwhile, at part load conditions, the controllable valve elements 51 can be re-configured during operational conditions and then operated or configured such that the first hydraulic chambers 53 are fluidly communicative with the cooler 14 and the second hydraulic chambers 55 are fluidly communicative with the condenser 13. This arrangement causes the pistons 42 to move in the forward direction and thus urges the head 41 to move into the first channel 31 toward the diffuser full-closed position.

(22) In the case of the additional piping 56 extending between each of the controllable valve elements 51 and the oil sump 150 and the outlet of the pump 151, the controllable valve elements 51 may be operable such that the diffuser full-open and the diffuser full-closed positions are achievable.

(23) For example, at 75%/100% load capacity conditions, the controllable valve elements 51 can be operated or configured such that the first hydraulic chambers 53 are fluidly communicative with the outlet of the pump 151 and the second hydraulic chambers 55 are fluidly communicative with the oil sump 150. This arrangement causes the pistons 42 to move in the reverse or rearward direction and thus urges the head 41 to retract in the reverse or rearward direction from the first channel 31 toward the diffuser full-open position. Meanwhile, at part load conditions, the controllable valve elements 51 can be re-configured during operational conditions and then operated or configured such that the first hydraulic chambers 53 are fluidly communicative with the oil sump 150 and the second hydraulic chambers 55 are fluidly communicative with the outlet of the pump 151. This arrangement causes the pistons 42 to move in the forward direction and thus urges the head 41 to move into the first channel 31 toward the diffuser full-closed position.

(24) In accordance with exemplary embodiments and, as shown in FIG. 3, the pistons 42 may each be provided as multiple pistons 42 with the drive system 50 being characterized in that the third channel 33 is fluidly communicative with at least one of the cooler 14 and the condenser 13 (see FIG. 1) and with the oil sump 150 and an outlet of the pump 151 (see FIG. 1). The drive system 50 therefore may include: the controllable valve element 51, first piping 52 between the controllable valve element 51 and a first hydraulic chamber 53 of the third channel 33, second piping 54 between the controllable valve element 51 and a second hydraulic chamber 55 of the third channel 33, third piping 57 between the controllable valve element 51 and a third hydraulic chamber 58 of the third channel 33, and fourth piping 59 between the controllable valve element 51 and a fourth hydraulic chamber 60 of the third channel 33. The drive system 50 may also include the additional piping 56 between the controllable valve element 51 and the cooler 14 and the condenser 13 or between the controllable valve element 51 and the oil sump 150 and the outlet of the pump 151.

(25) In the case of the additional piping 56 extending between each of the controllable valve elements 51 and the cooler 14 and the condenser 13, the controllable valve elements 51 may be operable such that the diffuser full-open and the diffuser full-closed positions are achievable.

(26) For example, at 75%/100% load capacity conditions, the controllable valve elements 51 can be operated or configured such that the first hydraulic chambers 53 are fluidly communicative with the condenser 13 and the second, third and fourth hydraulic chambers 55, 58 and 60 are fluidly communicative with the cooler 14. This arrangement causes the pistons 42 to move in the reverse or rearward direction and thus urges the head 41 to retract in the reverse or rearward direction from the first channel 31 toward the diffuser full-open position. Meanwhile, at 50% load capacity conditions, the controllable valve elements 51 can be re-configured during operational conditions and then operated or configured such that the first, second and third hydraulic chambers 53, 55 and 58 are fluidly communicative with the cooler 14 and the fourth hydraulic chambers 60 are fluidly communicative with the condenser 13. This arrangement causes the pistons 42 to move in the forward direction and thus urges the head 41 to move into the first channel 31 toward a diffuser partial-closed position. At part load or 25% load capacity conditions, the controllable valve elements 51 can be re-configured during operational conditions and then operated or configured such that only the second hydraulic chambers 55 are fluidly communicative with the condenser 13 and the first, third and fourth hydraulic chambers 53, 58 and 60 are fluidly communicative with the cooler 14. This arrangement causes the pistons 42 to move in the forward direction and thus urges the head 41 to move into the first channel 31 toward a diffuser full-closed position.

(27) In accordance with exemplary embodiments and, as shown in FIG. 4, the drive system 50 may include motors 65 that are respectively disposable in each of the third channels 33. These motors 65 may be provided, for example, as linear motor actuators. They are each receptive of power and signal data from a controller 66 by way of wired or wireless communication lines 67 and 68 and are configured to apply a motorized drive to the pistons 42 as described herein.

(28) In accordance with further embodiments and, as shown in FIG. 2 the variable diffuser drive system 100 may also include a position sensor 110 (it is to be understood that the position sensor 110 can be provided in any of the embodiments described herein and is included only in FIG. 2 for illustrative purposes). The position sensor 110 can be disposed and configured to sense a position of the annular body 410 (see FIG. 5) of the head 41 so that the sensed position can be employed in a feedback control loop that allows for greater control over operations of the variable diffuser drive system 100.

(29) That is, with reference to FIG. 6, the variable diffuser drive system 100 may also include a control element 120 that is disposed in signal communication with the position sensor 110 and with the controllable valve elements 51 of FIGS. 2 and 3 or with the controller 61 of FIG. 4. As shown in FIG. 6, the control element 120 may include a processing unit 121, a memory unit 122 and a networking unit 123 by which the processing unit 121 is communicative with the position sensor 100 and the controllable valve element 51 or the controller 61. The memory unit 122 has executable instructions stored thereon, which are readable and executable by the processing unit 121. When the executable instructions are read and executed by the processing unit 121, the executable instructions cause the processing unit 121 to operate as described herein.

(30) With reference to FIG. 7, a method of operating the variable diffuser drive system 100 described herein is provided. The method includes determining a load condition of the centrifugal compressor (block 701), calculating a target position of the head 41 of the gas or oil actuator 40 to achieve a certain degree of variable diffusion for the determined load condition (block 702) and configuring or re-configuring the drive system 50 to drive (e.g., by hydraulic or motorized driving) forward and reverse movements of the pistons 42 in the third channels 33 in concert with one another toward and away from positions at which the head 41 at least partially blocks the first channel 31 in accordance with the determined load condition (block 703). The method further includes sensing an amount of diffusion achieved by the driving of block 703 and determining an actual position of the head 41 of the gas or oil actuator 40 or sensing an actual displacement of the head 41 of the gas or oil actuator 40 by the position sensor 110 of FIG. 1 (block 704) and correcting the driving to an extent that the actual position of the head 41 differs from the target position (block 705).

(31) Benefits of the features described above are a reduced number of components and increased simplicity with lowered costs as well as increased reliability and simplified design.

(32) While the disclosure is provided in detail in connection with only a limited number of embodiments, it should be readily understood that the disclosure is not limited to such disclosed embodiments. Rather, the disclosure can be modified to incorporate any number of variations, alterations, substitutions or equivalent arrangements not heretofore described, but which are commensurate with the spirit and scope of the disclosure. Additionally, while various embodiments of the disclosure have been described, it is to be understood that the exemplary embodiment(s) may include only some of the described exemplary aspects. Accordingly, the disclosure is not to be seen as limited by the foregoing description, but is only limited by the scope of the appended claims.