Linkage adjusting device for air inlet guide vane and variable-width diffuser of compressor
The nested two-stage cylinders and hydraulic system jointly adjust the intake guide vanes and the variable-width diffuser, solving the problem of poor diffuser flow channel width and improving the performance and stability of the compressor.
Patent Information
- Application Number
- CN202422753458.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-12
- Publication Date
- 2025-10-10
- Estimated Expiration
- 2034-11-12
AI Technical Summary
The diffuser flow passage width of existing centrifugal compressors cannot be at the optimal position, resulting in local vortex and affecting the performance of the compressor.
The nested two-stage oil cylinder and hydraulic system are used to adjust the intake guide vanes and the variable width diffuser in a coordinated manner. The position of the piston is controlled by the hydraulic system to achieve coordinated adjustment of the intake guide vanes and the variable width diffuser.
The VGD maintains the optimal position at medium and high loads without affecting performance, and works together with the IGV at low loads to improve the performance and stability of the compressor.
Smart Images
Figure CN223424318U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of centrifugal compressors, in particular to a linkage regulating device for an air intake guide vane and a variable width diffuser of a compressor. Background Art
[0002] In addition to changing the impeller's operating speed through frequency conversion, the workload regulation of a centrifugal compressor is generally achieved by adjusting the inlet guide vanes (IGV) and the variable geometry diffuser (VGD) in the compressor structure. IGVs and VGDs usually have two forms of motion: separate motion or combined motion. Separate motion usually requires the installation of two linear motors or rotary motion to drive the IGV and VGD respectively. Combined motion uses a hydraulic or pneumatic piston to drive the actuator to make the IGV and VGD move together according to the relationship determined by the design.
[0003] Existing linkage mechanisms typically use a single piston to simultaneously drive the crank-connecting rod mechanism of the IGV and VGD. This ensures that the VGD always moves in conjunction with the IGV in a fixed, designed relationship. This design has two drawbacks: first, the VGD motion mechanism is complex, with numerous components and high cost; second, under medium and high loads, the VGD passively opens or closes, failing to maintain its optimal position, thus impacting compressor performance.
[0004] like Figure 1 As shown in the figure, at maximum load, the IGV is fully opened, but the VGD exceeds the diffuser flow path width, creating a "dimple" in the diffuser flow path. This creates localized vortices, affecting diffusion capability and ultimately compressor performance. Similarly, if the VGD is designed to be flush with the diffuser flow path when the IGV is fully opened, then when the IGV is slightly closed to reduce load to medium or high loads, the VGD will begin to close, creating a "bump" in the diffuser flow path, also causing localized vortices and affecting performance. Summary of the Invention
[0005] The purpose of the utility model is to overcome the deficiencies in the prior art and provide a linkage adjustment device for the intake guide vanes and the variable width diffuser of a compressor, so as to solve the technical problem that the flow channel width of the diffuser of the existing centrifugal compressor cannot be in the optimal position, resulting in "bosses" or "pits" and affecting the performance of the compressor.
[0006] In order to achieve the above purpose, the present invention adopts the following technical solutions:
[0007] The utility model provides a linkage adjustment device for an intake guide vane and a variable-width diffuser of a compressor, comprising a nested two-stage oil cylinder and a hydraulic system, wherein the nested two-stage oil cylinder comprises a cylinder body, a first piston member and a second piston member, the first piston member and the second piston member are sequentially embedded in the inner wall of the cylinder body, a first chamber is formed between the first piston member and the cylinder body, a second chamber is formed between the first piston member, the second piston member and the cylinder body, and a third chamber is formed between the second piston member and the cylinder body; the first piston member close to one end of the diffuser flow channel serves as the variable-width diffuser, and the second piston member is connected to the intake guide vane via a crank; the hydraulic system is respectively connected to the first chamber, the second chamber and the third chamber.
[0008] Optionally, the cylinder body is arranged on the inner wall of the compressor shell or is integrally formed with the compressor shell.
[0009] Optionally, the cylinder body, the first piston member and the second piston member are coaxial rotating body structures, with raised portions at both ends of the cylinder body, the first piston member including a first piston and a first piston rod, and the second piston member including a second piston and a second piston rod; the first piston rod and the second piston rod are respectively embedded in the raised portions at both ends of the cylinder body; the first piston is embedded between the cylinder body and the second piston rod and is fixedly connected to the first piston rod; the second piston is embedded in the cylinder body and is fixedly connected to the second piston rod.
[0010] Optionally, the first piston rod serves as a variable width diffuser at one end close to the diffuser flow channel, and the second piston rod is provided with a groove on the side away from the cylinder body. The crank includes a fixed arm, and the two ends of the fixed arm are respectively provided with a first connecting arm and a second connecting arm in opposite directions and perpendicular to the fixed arm. The first connecting arm is provided in the groove, and the second connecting arm is fixedly connected to the intake guide vane.
[0011] Optionally, the hydraulic system includes a first three-position four-way reversing valve, a second three-position four-way reversing valve, an oil pump and an oil tank, the P ports of the first three-position four-way reversing valve and the second three-position four-way reversing valve are connected to the oil tank through the oil pump, the T ports are connected to the oil tank, the B ports are connected to the third chamber, and the A ports of the first three-position four-way reversing valve and the second three-position four-way reversing valve are connected to the first chamber and the second chamber respectively.
[0012] Optionally, an oil filter is further provided at the outlet of the oil pump.
[0013] Optionally, a displacement sensor is provided on the second piston member, and the displacements of the first piston member and the second piston member are obtained through detection values of the displacement sensor.
[0014] Optionally, the starting point and the end point of the stroke of the first piston member and the second piston member are determined by the starting point and the end point of the opening of the variable width diffuser and the intake guide vane.
[0015] Compared with the prior art, the present invention has the following beneficial effects:
[0016] The utility model provides a linkage adjustment device for the intake guide vanes and the variable width diffuser of a compressor, which adopts an integrated nested two-stage oil cylinder to simultaneously adjust the intake guide vanes and the variable width diffuser in a linkage manner. It not only has a simple and compact structure and reliable and stable operation, but also has a low production cost and is easy to promote and apply.
[0017] Different from the existing technology that adopts a fixed linkage relationship between the intake guide vanes and the variable width diffuser, the linkage structure of the utility model enables the VGD to remain flush with the flow channel at medium and high loads of the compressor, always in the optimal position without affecting the performance. Under low loads, it works together with the IGV to achieve airflow regulation and anti-surge control, which can effectively improve the performance and stability of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS
[0018] Figure 1 It is a structural diagram of the "pit area" caused by the VGD position under high load provided in the background technology of the utility model;
[0019] Figure 2 This is a schematic structural diagram of the linkage adjustment device of the intake guide vane and the variable width diffuser of the compressor provided by the utility model;
[0020] Figure 3 This is a schematic diagram of the linkage relationship between the intake guide vanes and the variable width diffuser provided by the utility model;
[0021] The following are marked in the figure:
[0022] 1. Inspiratory vertebral segment; 11. Intake guide vane;
[0023] 2. Impeller;
[0024] 3. Diffuser flow channel; 31. Variable width diffuser;
[0025] 4. Snail chamber;
[0026] 5. Nested two-stage oil cylinder; 51. Cylinder body; 52. First piston member; 521. First piston; 522. First piston rod; 53. Second piston member; 531. First piston; 532. Second piston rod; 533. Groove; 54. First chamber; 55. Second chamber; 56. Third chamber;
[0027] 6. Hydraulic system; 61. First three-position four-way reversing valve; 62. Second three-position four-way reversing valve; 63. Oil pump; 64. Oil tank; 65. Oil filter; 66. First oil circuit; 67. Second oil circuit; 68. Third oil circuit;
[0028] 7. Crank; 71. Fixed arm; 72. First connecting arm; 73. Second connecting arm;
[0029] 8. Shell. DETAILED DESCRIPTION
[0030] The present invention will be further described below in conjunction with the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention and are not intended to limit the scope of protection of the present invention.
[0031] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, features defined as "first", "second", etc. may explicitly or implicitly include one or more of the features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.
[0032] In the description of this utility model, it should be noted that, unless otherwise expressly specified or limited, the terms "installed," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections, electrical connections; direct connections, indirect connections through an intermediate medium, and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on specific circumstances.
[0033] Example 1:
[0034] like Figure 1As shown, an embodiment of the present invention provides a linkage adjustment device for the intake guide vanes and variable width diffuser of a compressor, which is applied to a centrifugal compressor. The gas enters the impeller 2 from the intake cone 1 through the intake guide vanes 11. After coming out of the impeller 2, the gas enters the volute 4 from the diffuser flow channel 3 through the variable width diffuser 31. The linkage adjustment device provided in this embodiment includes a nested two-stage oil cylinder 5 and a hydraulic system 6. The nested two-stage oil cylinder 5 includes a cylinder body 51, a first piston member 52 and a second piston member 53. The first piston member 52 and the second piston member 53 are sequentially embedded in the inner wall of the cylinder body 51. A first chamber 54 is formed between the first piston member 52 and the cylinder body 51, a second chamber 55 is formed between the first piston member 52, the second piston member 53 and the cylinder body 51, and a third chamber 56 is formed between the second piston member 53 and the cylinder body 51; the first piston member 52 is close to one end of the diffuser flow channel 3 as a variable width diffuser 31, and the second piston member 53 is connected to the intake guide vane 11 through the crank 7; the hydraulic system 6 is connected to the first chamber 54, the second chamber 55 and the third chamber 56 respectively. During operation, the hydraulic system 6 supplies and returns oil to the first chamber 54, the second chamber 55 and the third chamber 56, thereby changing the positions of the first piston member 52 and the second piston member 53, and adjusting the openings of the variable width diffuser 31 and the intake guide vanes 11 respectively through the first piston member 52 and the second piston member 53.
[0035] Specifically, in this embodiment, the cylinder body 51 is disposed on the inner wall of the compressor housing 8 or is integrally formed with the compressor housing 8. The cylinder body 51 can be fixed to the inner wall of the compressor housing 8 by assembly, facilitating assembly and maintenance. The cylinder body 51 can also be integrally formed with the compressor housing 8 to increase integration and reduce space usage. In other optional embodiments, the cylinder body 51 can also be fixed in other ways.
[0036] Specifically in this embodiment, the cylinder body 51, the first piston member 52 and the second piston member 53 are coaxial rotating body structures, and a protrusion is provided at both ends of the cylinder body 51. The first piston member 52 includes a first piston 521 and a first piston rod 522, and the second piston member 53 includes a second piston 531 and a second piston rod 532; the first piston rod 522 and the second piston rod 532 are respectively embedded in the protrusions at both ends of the cylinder body 51; the first piston 521 is embedded between the cylinder body 51 and the second piston rod 532, and is fixedly connected to the first piston rod 522; the second piston 531 is embedded in the cylinder body 51 and is fixedly connected to the second piston rod 532. The first piston rod 522 is close to the diffuser flow channel 3 at one end and serves as a variable width diffuser 31. The second piston rod 532 is provided with a groove 533 on the side away from the cylinder body 51. The crank 7 includes a fixed arm 71. The two ends of the fixed arm 71 are respectively provided with a first connecting arm 72 and a second connecting arm 73 in opposite directions and perpendicular to the fixed arm 71. The first connecting arm 72 is arranged in the groove 533, and the second connecting arm 73 is fixedly connected to the intake guide vane 11.
[0037] Specifically, in this embodiment, the hydraulic system 6 includes a first, third, and fourth-way reversing valve 61, a second, third, and fourth-way reversing valve 62, an oil pump 63, and an oil tank 64. Ports P of the first, third, and fourth-way reversing valves 61 and 62 are both connected to the oil tank 64 via the oil pump 63, ports T are both connected to the oil tank 64, and ports B are both connected to the third chamber 56. Ports A of the first, third, and fourth-way reversing valves 61 and 62 are connected to the first and second chambers 54 and 55, respectively. The oil ports of the first and third chambers 54 and 56 can be located in the raised portion of the cylinder body 51 to avoid affecting the travel of the first and second piston members 52 and 53. The oil port of the second chamber 55 can be located in the middle of the cylinder body 51. Its position needs to be determined based on the travel of the first and second piston members 52 and 53 to avoid blockage caused by alignment during movement of the first and second piston members 52 and 53. An oil filter 65 is further provided at the outlet of the oil pump 63 , and the oil filter 65 filters impurities in the hydraulic oil to keep the oil clean, thereby ensuring the stable operation of the hydraulic system 6 .
[0038] The working principle of this embodiment is as follows:
[0039] When the compressor stops, all oil circuits of the first three-position four-way reversing valve 61 and the second three-position four-way reversing valve 62 are de-energized and closed, the first piston 531 and the second piston 532 are both located at the rightmost end, the first piston rod 522 and the second piston rod 523 are at the rightmost end, and the variable width diffuser 31 and the intake guide vane 11 are both closed to the minimum.
[0040] When the compressor is increasing load from low load, the right side of the first, three-position, four-way reversing valve 61 is energized, while the second, three-position, four-way reversing valve 62 is de-energized. The oil supply port P1 is connected to the working port A1, and the oil return port T1 is connected to the working port B1. Hydraulic oil enters the first chamber 54 along the first oil path 66, pushing the first and second pistons 521, 531 to the left. The first and second pistons 521, 531 remain in contact, increasing the opening of the variable-width diffuser 31 and the intake guide vanes 11. The hydraulic oil in the third chamber 56 returns to the oil tank 64 via the third oil path 68. When the first piston 521 reaches a stroke of X1, the first piston rod 522 opens to its maximum position, and the variable-width diffuser 31 opens to its maximum position, flush with the diffuser flow channel 3, and the compressor increases to a medium load.
[0041] Afterward, the compressor continues to increase its load at medium to high levels. The first, three-position, four-way reversing valve 61 is de-energized, while the right side of the second, three-position, four-way reversing valve 62 is energized. The oil supply port P2 is connected to the working port A2, and the oil return port T2 is connected to the working port B2. Hydraulic oil flows along the second oil passage 67 into the second chamber 55, pushing the second piston 531 to continue moving leftward. The second piston rod 532 continues to increase the opening of the intake guide vanes 11, while the variable-width diffuser 31 remains stationary. When the third chamber 56 decreases to a value of X3 equal to zero, the compressor reaches its maximum load.
[0042] The same principle applies to compressor load shedding. During medium-to-high load shedding, the first, third, and fourth-way reversing valve 61 is de-energized, while the left side of the second, third, and fourth-way reversing valve 62 is energized. This connects the oil supply port P2 to the working port B2, and the oil return port T2 to the working port A2. Hydraulic oil enters the third chamber 56, pushing the second piston 531 rightward. This causes the hydraulic oil in the second chamber 55 to be discharged back to the oil tank 64 via the second oil passage 67. The second piston rod 532 then drives the intake guide vanes 11 to open more narrowly. The first piston 521 remains stationary, and the variable-width diffuser 31 remains stationary, until the first piston 521 and the second piston 531 engage. When continuing to reduce the load at low load, the second three-position four-way reversing valve 62 is de-energized, the left side of the first three-position four-way reversing valve 61 is energized, the oil supply port P1 is connected to the working port B1, and the oil return port T1 is connected to the working port A1, and the hydraulic oil enters the third chamber 56, pushing the second piston 531 and the first piston 521 to move to the right together, and the oil in the first chamber 54 is discharged back to the oil tank 64 through the first oil passage 66.
[0043] The second piston member 53 is provided with a displacement sensor, and the displacement of the first piston member 52 and the second piston member 53 is obtained by the detection value of the displacement sensor. The angle relationship between the intake guide vane 11 and the position of the variable width diffuser 31 under various loads can be clearly determined, such as Figure 3 At low loads, the intake guide vanes 11 and the variable width diffuser 31 operate in conjunction with each other, while at medium and high loads, the intake guide vanes 11 operate while the variable width diffuser 31 remains stationary.
[0044] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the technical principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.
Claims
1. A linkage adjustment device for an intake guide vane and a variable width diffuser of a compressor, characterized in that: It comprises a nested two-stage oil cylinder and a hydraulic system, wherein the nested two-stage oil cylinder comprises a cylinder body, a first piston member and a second piston member, wherein the first piston member and the second piston member are sequentially embedded in the inner wall of the cylinder body, a first chamber is formed between the first piston member and the cylinder body, a second chamber is formed between the first piston member, the second piston member and the cylinder body, and a third chamber is formed between the second piston member and the cylinder body; the first piston member serves as a variable-width diffuser near one end of the diffuser flow channel, and the second piston member is connected to the intake guide vane via a crank; the hydraulic system is respectively connected to the first chamber, the second chamber and the third chamber.
2. The compressor intake guide vane and variable width diffuser linkage adjustment device according to claim 1, characterized in that: The cylinder body is arranged on the inner wall of the compressor shell or is integrally formed with the compressor shell.
3. The compressor intake guide vane and variable width diffuser linkage adjustment device according to claim 1, characterized in that: The cylinder body, the first piston member and the second piston member are coaxial rotating body structures, and a protrusion is provided at both ends of the cylinder body. The first piston member includes a first piston and a first piston rod, and the second piston member includes a second piston and a second piston rod; the first piston rod and the second piston rod are respectively embedded in the protrusions at both ends of the cylinder body; the first piston is embedded between the cylinder body and the second piston rod and is fixedly connected to the first piston rod; the second piston is embedded in the cylinder body and is fixedly connected to the second piston rod.
4. The compressor intake guide vane and variable width diffuser linkage adjustment device according to claim 3, characterized in that: One end of the first piston rod close to the diffuser flow channel serves as a variable width diffuser, and a groove is provided on the side of the second piston rod away from the cylinder body. The crank includes a fixed arm, and both ends of the fixed arm are respectively provided with a first connecting arm and a second connecting arm in opposite directions and perpendicular to the fixed arm. The first connecting arm is arranged in the groove, and the second connecting arm is fixedly connected to the intake guide vane.
5. The compressor intake guide vane and variable width diffuser linkage adjustment device according to claim 1, characterized in that: The hydraulic system includes a first, three-position, four-way reversing valve, a second, three-position, four-way reversing valve, an oil pump and an oil tank. The P ports of the first, three-position, four-way reversing valve and the second, three-position, four-way reversing valve are connected to the oil tank through the oil pump, the T ports are connected to the oil tank, the B ports are connected to the third chamber, and the A ports of the first, three-position, four-way reversing valve and the second, three-position, four-way reversing valve are connected to the first chamber and the second chamber, respectively.
6. The compressor intake guide vane and variable width diffuser linkage adjustment device according to claim 5, characterized in that: An oil filter is also provided at the outlet of the oil pump.
7. The compressor intake guide vane and variable width diffuser linkage adjustment device according to claim 1, characterized in that: The second piston member is provided with a displacement sensor, and the displacements of the first piston member and the second piston member are obtained through detection values of the displacement sensor.
8. The compressor intake guide vane and variable width diffuser linkage adjustment device according to claim 1, characterized in that: The starting point and the ending point of the stroke of the first piston member and the second piston member are determined by the starting point and the ending point of the opening of the variable width diffuser and the intake guide vane.