Centrifugal compressor

Abstract

This application relates to the field of compressor technology and discloses a centrifugal compressor, including: an impeller assembly, including a main shaft, a disc, and a blade section; the disc is sleeved on the main shaft, and the blade section includes rigid blades and flexible blades; a plurality of rigid blades are uniformly fixed around the main shaft to the disc, and the first side of each rigid blade faces the main shaft, and its second side faces the edge of the disc; wherein, a receiving groove is formed on the second side of each rigid blade, and a flexible blade is correspondingly provided for each rigid blade, and the first side of the flexible blade extends into the receiving groove, and its second side is movably connected to the edge of the disc; and the movement direction of the second side of the flexible blade is limited to moving along the edge of the disc, the movement angle of the second side of each flexible blade is the same, and when the movement reaches the maximum angle, the first side of the flexible blade is still located in the receiving groove, thereby adjusting the outlet installation angle of the flexible blade by changing the movement angle of the second side of the flexible blade, thereby reducing the impact on the next stage blade section.

Description

Technical Field

[0001] This application relates to the field of compressor technology, for example to a centrifugal compressor. Background Technology

[0002] The centrifugal compressor is the core component of a chiller unit. Low-temperature, low-pressure refrigerant gas is compressed by the centrifugal compressor into high-temperature, high-pressure refrigerant gas. This high-temperature, high-pressure refrigerant gas then passes through a condenser, carrying away heat and condensing into high-temperature, high-pressure refrigerant liquid. The refrigerant liquid undergoes isenthalpic expansion through expansion valves and other expansion devices, becoming a low-temperature, low-pressure refrigerant gas-liquid mixture. This mixture enters the evaporator, absorbs heat, and evaporates back into low-temperature, low-pressure refrigerant gas. The refrigerant gas is then drawn back into the centrifugal compressor for compression, entering the next cycle. It can be seen that the efficiency of the centrifugal compressor directly affects the energy efficiency of the chiller unit.

[0003] The related technology discloses a centrifugal compressor in which the impeller blades have a locally flexible structure. This locally flexible structure is located on the non-working surface of the blade, is not parallel to the leading edge of the blade, and starts from the tail of the blade, tilting towards the middle of the blade as the blade height increases. The locally flexible structure of the novel blade interacts with the fluid within the impeller flow channel to delay flow separation within the flow channel. Especially under unstable operating conditions and when the flow rate deviates from the high-efficiency operating condition, the adaptive characteristics of the flexible structure can reduce fluid energy loss, thereby achieving the goal of stabilizing and improving the efficiency of the centrifugal compressor.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] The impeller's outlet installation angle is a fixed value and cannot be adjusted. In centrifugal compressors with multi-stage pressurization, when the rotational speed remains constant and only the gas flow rate increases or decreases, the airflow from the previous stage impeller will impact the next stage impeller, thus reducing the efficiency of the centrifugal compressor. Summary of the Invention

[0006] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0007] This disclosure provides a centrifugal compressor that solves the problem that the airflow from the upper stage impeller can impact the lower stage impeller.

[0008] In some embodiments, the centrifugal compressor includes:

[0009] An impeller assembly includes a main shaft, a disk, and a blade section; the disk is sleeved on the main shaft, and the blade section includes rigid blades and flexible blades;

[0010] Multiple rigid blades are uniformly fixed to the wheel disk around the main shaft, with the first side of each rigid blade facing the main shaft and the second side facing the edge of the wheel disk; wherein, the second side of each rigid blade is provided with a receiving groove, and each rigid blade is correspondingly provided with a flexible blade, with the first side of the flexible blade extending into the receiving groove and the second side movably connected to the edge of the wheel disk;

[0011] Furthermore, the movement direction of the second side of the flexible blade is limited to moving along the edge of the wheel. The movement angle of the second side of each flexible blade is the same, and when the movement reaches the maximum angle, the first side of the flexible blade is still located in the receiving groove. Thus, the outlet installation angle of the flexible blade is adjusted by changing the movement angle of the second side of the flexible blade.

[0012] Optionally, a traction shaft is connected to the second side of the flexible blade;

[0013] The edge of the wheel is provided with a through groove, which corresponds to the traction shaft, and the extension direction of the through groove is consistent with the movement direction of the second side of the flexible blade.

[0014] The traction shaft extends into the through groove and can move within the through groove, thereby driving the second side of the flexible blade to move synchronously.

[0015] Optionally, the centrifugal compressor further includes:

[0016] A movable component is used to drive the traction shaft to move within the through slot.

[0017] Optionally, the moving component includes:

[0018] Rotate the sleeve, which is fitted onto the main shaft and located on the side of the wheel disk away from the blade portion;

[0019] Multiple traction rods are evenly distributed along the outer surface of the rotating sleeve, and the first end of each traction rod is connected to the rotating sleeve, and the second end is connected to a traction shaft.

[0020] When the rotating sleeve rotates, it drives all the traction shafts to move synchronously through multiple traction rods.

[0021] Optionally, the traction shaft is parallel to the main shaft, and the first end of the traction shaft is connected to the flexible blade, and the second end extends into and out of the through groove;

[0022] The second end of the traction rod is connected to the second end of the traction shaft.

[0023] Optionally, the centrifugal compressor further includes:

[0024] A rotating assembly is used to drive the rotating sleeve to rotate.

[0025] Optionally, the rotating assembly includes:

[0026] A movable sleeve is fitted onto the main shaft and located between the inner side of the rotating sleeve and the main shaft; the movable sleeve can move along the main shaft, and its outer side is provided with a spiral groove;

[0027] The inner side of the rotating sleeve is provided with a connecting pin, which is located in the spiral groove; when the moving sleeve moves, it drives the connecting pin to move along the spiral groove, thereby driving the rotating sleeve to rotate.

[0028] Optionally, the spindle is provided with a guide member to guide the movable sleeve to move along the spindle.

[0029] Optionally, the centrifugal compressor further includes:

[0030] A drive component is used to move the movable sleeve.

[0031] Optionally, the movable sleeve has a narrow neck on the side away from the wheel, and a push ring is fitted onto the narrow neck; the drive assembly includes:

[0032] A piston hydraulic cylinder, wherein the piston rod is connected to the push ring, and the moving direction of the piston rod is consistent with the moving direction of the moving sleeve.

[0033] The centrifugal compressor provided in this embodiment can achieve the following technical effects:

[0034] The centrifugal compressor provided in this embodiment comprises rigid and flexible blades forming the blade section. When the blade section rotates at high speed, it accelerates the gas and throws it into the diffuser to achieve pressurization. When the centrifugal compressor's rotational speed u remains constant, but the gas flow rate w increases or decreases, with the outlet installation angle β remaining constant, the direction of the combined gas velocity c (u and w) deviates from its original direction, thus impacting the next stage blade section. At this time, the second side of the flexible blade is moved, and a portion of the first side of the flexible blade is extracted from the receiving groove, while the outlet installation angle β of the flexible blade changes. The specific angle of movement of the second side of the flexible blade is adjusted according to the change in gas flow rate w. The goal of this adjustment is to restore the direction of the combined gas velocity c to its original direction by changing the outlet installation angle β, thereby reducing the impact on the next stage blade section and effectively improving the efficiency of the centrifugal compressor. Furthermore, when the flexible blade moves to its maximum angle, its first side remains within the receiving groove, thus maintaining the integrity of the blade section composed of the rigid and flexible blades.

[0035] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0036] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0037] Figure 1 This is a schematic diagram of the structure of the impeller assembly provided in the embodiments of this disclosure;

[0038] Figure 2 yes Figure 1 Enlarged view of part A;

[0039] Figure 3 yes Figure 1 Enlarged view of part B;

[0040] Figure 4 This is a schematic diagram of the blade section provided in an embodiment of this disclosure;

[0041] Figure 5 yes Figure 4 Enlarged view of part C;

[0042] Figure 6 This is a cross-sectional schematic diagram of the impeller assembly provided in an embodiment of this disclosure;

[0043] Figure 7 yes Figure 6 Enlarged view of part D;

[0044] Figure 8 yes Figure 6 Enlarged view of part E;

[0045] Figure 9 This is a schematic diagram of the synthetic gas flow velocity provided in an embodiment of this disclosure;

[0046] Figure 10 This is a schematic diagram of the outlet installation angle under the first operating condition provided in this embodiment of the disclosure;

[0047] Figure 11 This is a schematic diagram showing that the outlet installation angle has not been adjusted under the second operating condition provided in this embodiment of the disclosure;

[0048] Figure 12 This is a schematic diagram of the outlet installation angle after adjustment under the second operating condition provided in the embodiments of this disclosure.

[0049] Figure label:

[0050] 100: Blade section; 110: Rigid blade; 111: Receiving groove; 120: Flexible blade; 121: Traction shaft; 130: Wheel disc; 131: Front disc body; 132: Rear disc body; 133: Through groove;

[0051] 200: Rotating sleeve; 210: Traction rod; 220: Connecting pin;

[0052] 300: Moving sleeve; 310: Spiral groove; 320: Guide groove; 330: Neck;

[0053] 400: Spindle; 410: Guide pillar;

[0054] 500: Piston hydraulic cylinder; 510: Piston rod; 520: Push ring; 530: Push rod. Detailed Implementation

[0055] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0056] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0057] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0058] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0059] Unless otherwise stated, the term "multiple" means two or more.

[0060] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0061] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0062] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0063] The centrifugal compressor first accelerates the gas through the high-speed rotation of the first-stage impeller, throwing it into the first-stage diffuser. In the diffuser, the high-speed gas decelerates, and according to Bernoulli's principle, dynamic pressure is converted into static pressure, achieving the first stage of pressurization. The pressurized gas then passes through a first-stage bend and a first-stage return channel before entering the second-stage impeller, undergoing the same process to achieve second-stage pressurization. Furthermore, multiple impeller stages can be configured according to user needs, repeating the above process to achieve third-stage, fourth-stage, and other subsequent pressurization processes.

[0064] For the impeller of a centrifugal compressor, the linear velocity at its edge is denoted as u, and the velocity of the airflow relative to the impeller is denoted as w. According to the velocity triangle theorem, the combined velocity of u and w is denoted as c. The acute angle between c and the tangent to the impeller edge is denoted as γ, and the acute angle between w and the tangent to the impeller edge is denoted as β. β is called the impeller outlet installation angle. Figure 9 As shown.

[0065] This disclosure provides a centrifugal compressor, including an impeller assembly. The impeller assembly includes a main shaft 400, a disk 130, and a blade section 100; the disk 130 is sleeved on the main shaft 400, and the blade section 100 includes rigid blades 110 and flexible blades 120; as shown... Figure 4 As shown, multiple rigid blades 110 are uniformly fixed to the wheel 130 around the main shaft 400, with the first side of each rigid blade 110 facing the main shaft 400 and its second side facing the edge of the wheel 130; as Figure 5As shown, each rigid blade 110 has a receiving groove 111 on its second side, and each rigid blade 110 is correspondingly provided with a flexible blade 120. The first side of the flexible blade 120 extends into the receiving groove 111, and its second side is movably connected to the edge of the wheel 130. Furthermore, the movement direction of the second side of the flexible blade 120 is limited to moving along the edge of the wheel 130. The movement angle of the second side of each flexible blade 120 is the same, and when it moves to the maximum angle, the first side of the flexible blade 120 is still located in the receiving groove 111. Thus, the outlet installation angle of the flexible blade 120 is adjusted by changing the movement angle of the second side of the flexible blade 120.

[0066] The centrifugal compressor provided in this embodiment comprises a blade section 100 consisting of rigid blades 110 and flexible blades 120. When the blade section 100 rotates at high speed, it accelerates the gas and throws it into the diffuser to achieve pressurization. When the centrifugal compressor's rotational speed u remains constant, but the gas flow rate w increases or decreases, and the outlet installation angle β remains constant, the direction of the combined gas velocity c of u and w deviates from its original direction, thus impacting the next-stage blade section 100. At this time, the second side of the flexible blade 120 is moved, and while a portion of the first side of the flexible blade 120 is extracted from the receiving groove 111, the outlet installation angle β of the flexible blade 120 changes. The moving angle of the second side of the flexible blade 120 is specifically adjusted according to the change in gas flow rate w. The goal of this adjustment is to restore the direction of the combined gas velocity c to its original direction by changing the outlet installation angle β, thereby reducing the impact on the next-stage blade section 100 and effectively improving the efficiency of the centrifugal compressor. Furthermore, when the flexible blade 120 moves to its maximum angle, its first side remains within the receiving groove 111, thus maintaining the integrity of the blade section 100 composed of the rigid blade 110 and the flexible blade 120.

[0067] Optionally, such as Figure 2 As shown, a traction shaft 121 is connected to the second side of the flexible blade 120; a through groove 133 is provided on the edge of the wheel 130, the through groove 133 corresponds to the traction shaft 121, and the extension direction of the through groove 133 is consistent with the movement direction of the second side of the flexible blade 120; the traction shaft 121 extends into the through groove 133 and can move within the through groove 133, thereby driving the second side of the flexible blade 120 to move synchronously.

[0068] In this embodiment, the wheel 130 includes a front disc body 131 and a rear disc body 132, with a through groove 133 on the rear disc body 132. Rigid blades 110 are connected to the front disc body 131 and the rear disc body 132 on both sides in the width direction. On both sides of the rigid blade 110 in the length direction, the first side faces the main shaft 400, and the second side faces the edge of the rear disc body 132. Flexible blades 120 have their first side extending into the receiving groove 111 of the rigid blade 110 on both sides in the length direction, and a traction shaft 121 is provided on their second side. The flexible blades 120 are abutted against the front disc body 131 and the rear disc body 132 on both sides in the width direction, and the front disc body 131 and the rear disc body 132 do not affect the movement of the flexible blades 120. The traction shaft 121 is parallel to the main shaft 400, and the first end of the traction shaft 121 is connected to the flexible blade 120, while the second end extends into the through groove 133.

[0069] For example, 12 rigid blades 110 are evenly arranged around the main shaft 400 on the rear disc body 132, and each rigid blade 110 corresponds to a flexible blade 120. 12 through slots 133 are evenly arranged at the edge of the rear disc body 132, and each through slot 133 corresponds to a flexible blade 120. The flexible blades 120 are movably connected to the corresponding through slots 133 via traction shafts 121.

[0070] Optionally, the width of the receiving groove 111 is adapted to the thickness of the flexible blade 120, and the depth of the receiving groove 111 is greater than or equal to the maximum moving distance of the second end of the flexible blade 120. This ensures that the length of the first side of the flexible blade 120 within the receiving groove 111 can meet the moving distance of the second side of the flexible blade 120.

[0071] Optionally, the length of the rigid blade 110 projected onto the rear disc 132 is 3 / 10 to 4 / 10 of the radius of the rear disc 132.

[0072] Optionally, the width of the moving slot is adapted to the diameter of the traction shaft 121 so that the traction shaft 121 can move smoothly within the moving slot. The length of the moving slot is 2 / 10 to 3 / 10 of the radius of the rear disc 132.

[0073] Optionally, the flexible blade 120 has a stop shaft on its first side, and a stop groove is provided on each of the opposite side walls of the receiving groove 111, with both ends of the stop shaft located in the two stop grooves respectively. When the first end of the flexible blade 120 moves, its second end moves synchronously and drives the stop shaft to move within the stop groove. Furthermore, the stop groove can prevent the second end of the flexible blade 120 from detaching from the receiving groove 111.

[0074] Optionally, the centrifugal compressor also includes a moving assembly. The moving assembly drives the traction shaft 121 to move within the through slot 133. Thus, as the traction shaft 121 moves, it causes the second end of the flexible blade 120 to move synchronously, and a portion of the first end of the flexible blade 120 extends from the receiving slot 111 to compensate for the movement of its first end. Simultaneously, the outlet installation angle β changes synchronously as the second end of the flexible blade 120 moves.

[0075] Optionally, such as Figure 3 As shown, the moving assembly includes a rotating sleeve 200 and multiple traction rods 210. The rotating sleeve 200 is sleeved on the main shaft 400 and located on the side of the wheel 130 away from the blade portion 100. The multiple traction rods 210 are evenly distributed along the outer surface of the rotating sleeve 200, and the first end of each traction rod 210 is connected to the rotating sleeve 200, and the second end is connected to a traction shaft 121. When the rotating sleeve 200 rotates, it drives all the traction shafts 121 to move synchronously through the multiple traction rods 210.

[0076] In this embodiment, the rear disc body 132 of the wheel 130 is provided with a through groove 133, and the rotating sleeve 200 is located on the side of the rear disc body 132 away from the blade portion 100. The first end of the rotating sleeve 200 is close to the rear disc body 132, and the second end is away from the rear disc body 132. Multiple traction rods 210 are evenly distributed along the side of the first end of the rotating sleeve 200. For example... Figure 7 As shown, the traction shaft 121 is parallel to the main shaft 400, and its first end is fixedly connected to the flexible blade 120, while its second end extends into and out of the through slot 133. The second end of the traction rod 210 is connected to the second end of the traction shaft 121. The traction rod 210 is abutted against the rear disc 132, and the end face of the first end of the rotating sleeve 200 is also abutted against the rear disc 132, thus ensuring the stability of the traction rod 210 as it rotates with the rotating sleeve 200. When the rotating sleeve 200 rotates, it drives all the traction rods 210 to rotate synchronously, thereby causing each traction rod 210 to move its corresponding traction shaft 121 within its corresponding through slot 133, thus synchronously changing the outlet installation angle β.

[0077] Optionally, the centrifugal compressor also includes a rotating assembly for driving the rotating sleeve 200 to rotate.

[0078] Optionally, such as Figure 3 and Figure 8As shown, the rotating assembly includes a movable sleeve 300. The movable sleeve 300 is sleeved on the main shaft 400 and is located between the inner side of the rotating sleeve 200 and the main shaft 400; the movable sleeve 300 can move along the main shaft 400, and its outer side is provided with a helical groove 310; the inner side of the rotating sleeve 200 is provided with a connecting pin 220, which is located in the helical groove 310; when the movable sleeve 300 moves, it drives the connecting pin 220 to move along the helical groove 310, thereby driving the rotating sleeve 200 to rotate.

[0079] In this embodiment, the outer diameter of the movable sleeve 300 is less than or equal to the inner diameter of the rotating sleeve 200, forming a connection where the movable sleeve 300 is sleeved on the main shaft 400 and the rotating sleeve 200 is sleeved on the movable sleeve 300. Furthermore, the connecting pin 220 on the inner side of the rotating sleeve 200 and the helical groove 310 on the outer side of the movable sleeve 300 form a sliding fit connection. When the movable sleeve 300 moves axially along the main shaft 400, i.e., the movable sleeve 300 performs linear motion, the connecting pin 220 slides along the helical groove 310. When the connecting pin 220 slides along the helical groove 310, since the helical groove 310 is evenly distributed around the outer cylindrical surface of the movable sleeve 300, the connecting pin 220 rotates around the outer cylindrical surface of the movable sleeve 300, thereby synchronously driving the rotating sleeve 200 to rotate axially around the main shaft 400. Thus, the linear motion of the movable sleeve 300 is converted into the rotational motion of the rotating sleeve 200. The number of spiral grooves 310 can be one or more. When there are multiple spiral grooves 310, the spiral directions of the multiple spiral grooves 310 are parallel, and the inner side of the rotating sleeve 200 is provided with connecting pins 220 corresponding to the multiple spiral grooves 310 respectively. This is beneficial to the rotational stability of the rotating sleeve 200.

[0080] Optionally, the main shaft 400 is provided with a guide member to guide the movable sleeve 300 to move along the main shaft 400. This makes the movement of the movable sleeve 300 smoother and more stable.

[0081] For example, a guide pin 410 is provided on the spindle 400, and a guide groove 320 corresponding to the guide pin 410 is provided on the inner side of the movable sleeve 300. The guide groove 320 is opened along the axial direction of the spindle 400. When the movable sleeve 300 is sleeved on the spindle 400, the guide pin 410 is located in the guide groove 320, thereby playing a guiding role. Furthermore, when the guide pin 410 abuts against the two ends of the guide groove 320, it can also form a limiting position.

[0082] Optionally, the centrifugal compressor also includes a drive assembly for moving the movable sleeve 300. In this way, the drive assembly moves the movable sleeve 300, which in turn rotates the rotating sleeve 200, which in turn moves all the traction shafts 121 synchronously, thereby adjusting the outlet installation angle β.

[0083] For example, such as Figure 6 and Figure 8 As shown, the movable sleeve 300 has a narrow neck 330 on the side away from the wheel 130, and a push ring 520 is fitted on the narrow neck 330; the drive assembly includes a piston hydraulic cylinder 500, the piston rod 510 of the piston hydraulic cylinder 500 is connected to the push ring 520, and the moving direction of the piston rod 510 is consistent with the moving direction of the movable sleeve 300.

[0084] In this embodiment, the push ring 520 is perpendicular to the axial direction of the main shaft 400, and a push rod 530 is connected to one side of the push ring 520, which is also perpendicular to the axial direction of the main shaft 400. The first end of the push rod 530 is connected to the push ring 520, and the second end is connected to the piston rod 510. When the piston rod 510 moves, its force is transmitted sequentially through the push rod 530 and the push ring 520 to the movable sleeve 300, thereby pushing the movable sleeve 300 to move axially along the main shaft 400.

[0085] In another example, an electric telescopic rod is connected to the side of the movable sleeve 300 away from the wheel 130, and the extension and retraction direction of the electric telescopic rod is consistent with the movement direction of the movable sleeve 300. When the electric telescopic rod extends or retracts, it can drive the movable sleeve 300 to move synchronously along the axial direction of the main shaft 400.

[0086] The following details the effect of the above embodiments on adjusting the outlet installation angle β:

[0087] Under the first operating condition, such as Figure 10 As shown, the linear velocity of the second edge of the flexible blade 120 is denoted as u1, the velocity of the airflow relative to the flexible blade 120 is denoted as w1, and the velocity of the combined gas is denoted as c1. The acute angle between c1 and the tangent of the edge of the flexible blade 120 is denoted as γ1, and the outlet installation angle of the flexible blade 120 is denoted as β1.

[0088] Under the second operating condition, the linear velocity of the second edge of the flexible blade 120 is denoted as u2, the velocity of the airflow relative to the flexible blade 120 is denoted as w2, and the velocity of the combined gas is denoted as c2. The acute angle between c2 and the tangent to the edge of the flexible blade 120 is denoted as γ2, and the outlet installation angle of the flexible blade 120 is denoted as β2. Here, u1 = u2, w2 > w1, meaning that compared to the first operating condition, the centrifugal compressor speed remains unchanged in the second operating condition, but the gas flow rate increases. When the centrifugal compressor switches from the first operating condition to the second operating condition, if the outlet installation angle of the flexible blade 120 remains unchanged, i.e., β2 = β1, then according to the velocity triangle theorem, γ2 > γ1, as... Figure 11 As shown. This changes the direction of c2, thus impacting the next stage blade section 100.

[0089] When the centrifugal compressor switches from the first operating condition to the second operating condition, in the case of the centrifugal compressor provided in this embodiment, the moving sleeve 300 is driven to move axially along the main shaft 400 by the drive assembly. When the moving sleeve 300 moves, it drives the rotating sleeve 200 to rotate. When the rotating sleeve 200 rotates, multiple traction rods 210 drive all traction shafts 121 to move synchronously within the through slot 133. The traction shafts 121 drive the corresponding flexible blades 120 to move synchronously, thereby adjusting the outlet installation angle of the flexible blades 120 to reduce β2, and reducing it to a point where γ2 = γ1. Figure 12 As shown, although the size of c2 increases, by adjusting β2, the direction of c2 is restored to the same direction as that of c1, thereby reducing the impact on the next stage blade section 100 and effectively improving the efficiency of the centrifugal compressor.

[0090] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A centrifugal compressor characterized by, Comprising: A impeller assembly, including a main shaft (400), a wheel disc (130) and a blade part (100); the wheel disc (130) is sleeved on the main shaft (400), and the blade part (100) includes rigid blades (110) and flexible blades (120); A plurality of the rigid blades (110) are fixed to the wheel disc (130) around the main shaft (400), and the first side of each rigid blade (110) faces the main shaft (400), and the second side faces the edge of the wheel disc (130); wherein the second side of each rigid blade (110) is provided with a receiving groove (111), and each rigid blade (110) is provided with a flexible blade (120), and the first side of the flexible blade (120) extends into the receiving groove (111), and the second side is movably connected to the edge of the wheel disc (130); And the moving direction of the second side of the flexible blade (120) is limited to moving along the edge of the wheel disc (130), the moving angle of the second side of each flexible blade (120) is the same, and when the second side of the flexible blade (120) moves to the maximum angle, the first side of the flexible blade (120) is still located in the receiving groove (111), so as to adjust the outlet installation angle of the flexible blade (120) by changing the moving angle of the second side of the flexible blade (120).

2. The centrifugal compressor according to claim 1, wherein The second side of the flexible blade (120) is connected with a traction shaft (121); The edge of the wheel disc (130) is provided with a through groove (133), the through groove (133) corresponds to the traction shaft (121), and the extension direction of the through groove (133) is consistent with the moving direction of the second side of the flexible blade (120); The traction shaft (121) extends into the through groove (133) and can move in the through groove (133), thereby driving the second side of the flexible blade (120) to move synchronously.

3. The centrifugal compressor of claim 2, wherein, Further comprising: A moving assembly for driving the traction shaft (121) to move in the through groove (133).

4. The centrifugal compressor of claim 3, wherein, The moving assembly comprises: A rotating sleeve (200) sleeved on the main shaft (400) and located on the side of the wheel disc (130) away from the blade part (100); A plurality of traction rods (210) are uniformly arranged along the outer side surface of the rotating sleeve (200), and the first end of each traction rod (210) is connected to the rotating sleeve (200), and the second end is connected to the traction shaft (121); When the rotating sleeve (200) rotates, all the traction shafts (121) are driven to move synchronously through the plurality of traction rods (210).

5. The centrifugal compressor according to claim 4, wherein The traction shaft (121) is parallel to the main shaft (400), and the first end of the traction shaft (121) is connected to the flexible blade (120), and the second end extends into and out of the through groove (133); The second end of the traction rod (210) is connected to the second end of the traction shaft (121).

6. The centrifugal compressor of claim 4 or 5, characterized in that Also comprising: a rotating assembly for driving the rotating sleeve (200) to rotate.

7. The centrifugal compressor of claim 6, wherein The rotating assembly comprises: a moving sleeve (300) sleeved on the main shaft (400) and located between the inner side of the rotating sleeve (200) and the main shaft (400); the moving sleeve (300) is movable along the main shaft (400), and the outer side of the moving sleeve (300) is provided with a helical groove (310); the inner side of the rotating sleeve (200) is provided with a connecting pin (220), and the connecting pin (220) is located in the helical groove (310); when the moving sleeve (300) moves, the connecting pin (220) moves along the helical groove (310), thereby driving the rotating sleeve (200) to rotate.

8. The centrifugal compressor according to claim 7, characterized in that the main shaft (400) is provided with a guide member for guiding the moving sleeve (300) to move along the main shaft (400).

9. The centrifugal compressor of claim 7 or 8, characterized in that Also comprising: a driving assembly for driving the moving sleeve (300) to move.

10. The centrifugal compressor of claim 9, wherein, the side of the moving sleeve (300) away from the wheel disc (130) is provided with a neck (330), and the neck (330) is sleeved with a pushing ring (520); the driving assembly comprises: a piston hydraulic cylinder (500), the piston rod (510) of which is connected to the pushing ring (520), and the moving direction of the piston rod (510) is consistent with the moving direction of the moving sleeve (300).

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