Modularized rotor assembly of turbo expander

Abstract

The invention relates to the technical field of turbo expanders, in particular to a modularized rotor assembly of a turbo expander. According to the technical scheme, the device comprises a bearing module, and a main shaft is installed in the bearing module in a penetrating mode; the two ends of the main shaft are detachably connected with first mounting cavities through connecting assemblies; a second mounting cavity is mounted on the outer wall of one end of the first mounting cavity, and acting blades are mounted on the outer side wall of the second mounting cavity at equal intervals; and one end of a transmission rod is detachably inserted into the second mounting cavity through a connecting assembly. Through the integrated design of a modular insertion structure, centrifugal locking and end face tooth cooperative torque transmission and negative thermal expansion NTE sleeve temperature change compensation, the operation stability under the high-rotation-speed working condition is remarkably improved while local rapid replacement and maintenance of the rotor are achieved, and the problem of pretightening force failure caused by cold contraction in the cryogenic environment is effectively solved.

Description

Technical Field

[0001] This invention relates to the field of turbine expander technology, and more particularly to a modular rotor assembly for a turbine expander. Background Technology

[0002] Turbine expanders (also known as expansion turbines) are the core rotating machines in cryogenic and energy systems that realize adiabatic expansion refrigeration and energy recovery. They output shaft work through the isentropic or near-isentropic expansion of high-pressure gas, while their own temperature drops sharply. Their efficiency is far superior to that of throttle valves, making them the "heart" of air separation, liquefied natural gas (LNG), and various cryogenic engineering fields.

[0003] As industrial equipment develops towards larger scale, integration, and higher efficiency, the operating conditions of turboexpanders are becoming increasingly demanding. Rotor speeds often reach tens of thousands of revolutions per minute, and operating temperatures cover a wide range from ambient to near absolute zero. Traditional turboexpander rotors typically employ an integral structure design, where the main shaft, impeller, and drive rod are formed as a single unit through forging or welding. However, this integral structure exhibits significant limitations in practical applications: First, it is difficult to manufacture and requires high machining precision. If a local area (such as impeller blades) is damaged, worn, or fails due to fatigue, the entire shaft often needs to be scrapped, resulting in significant resource waste and high costs for spare parts and maintenance. Second, under cryogenic conditions, the inconsistent shrinkage effects of different materials can easily lead to loosening of the connection preload, affecting the stability of rotor operation and sealing performance. Furthermore, the integral structure prevents targeted disassembly and replacement of failed components, resulting in long downtime for equipment maintenance and impacting production continuity.

[0004] A search revealed that Chinese patent literature discloses "A Rotor Shaft System Structure for a Large Turbine Expander" (Publication No.: CN116146290A). While this solution provides a shaft system structure with good repeatability of rotor dynamic balancing accuracy and improves the balancing problem of traditional shaft systems to some extent, it still adopts an integral or semi-integral design approach. Once local impeller damage or seal wear occurs, it is still difficult to achieve targeted and rapid replacement, resulting in high maintenance costs and significant resource waste. Therefore, this application proposes a modular rotor assembly for a turbine expander. Summary of the Invention

[0005] The purpose of this invention is to address the problem that traditional turbine expander rotors typically employ an integral structure design, which leads to high maintenance costs and significant resource waste once local impeller damage or seal wear occurs. This invention proposes a modular rotor assembly for turbine expanders.

[0006] The technical solution of the present invention: a modular rotor assembly for a turbine expander, comprising:

[0007] The bearing module has a main shaft installed through its interior;

[0008] Both ends of the spindle are detachably connected to a first mounting cavity via a connecting assembly;

[0009] A second mounting cavity is installed on one end of the outer wall of the first mounting cavity, and power blades are installed at equal intervals on the outer wall of the second mounting cavity.

[0010] One end of a transmission rod is detachably inserted into the interior of the second mounting cavity via a connecting assembly;

[0011] The transmission rod is fitted with an NTE sleeve, which is made of a negative thermal expansion material.

[0012] Optionally, the connection component includes:

[0013] The first connector is installed at the end of the spindle;

[0014] Multiple first centrifugal wedges are installed at equal intervals on the outer wall of the first plug-in block;

[0015] The first mounting cavity contains a first inclined block that mates with the first centrifugal wedge.

[0016] Optionally, a first elastic retaining ring for constraining the connecting assembly is installed on the outer wall of one end of the first mounting cavity.

[0017] Optionally, a snap-fit ​​block is provided at one end of the first mounting cavity, and a snap-fit ​​groove is provided at the end of the first insertion block away from the main shaft. The snap-fit ​​block engages with the snap-fit ​​groove to achieve circumferential positioning.

[0018] Optionally, the connecting component includes:

[0019] The second connector is inserted into the interior of the second mounting cavity;

[0020] Multiple second centrifugal wedges are installed at equal intervals on the outer side wall of the second plug-in block;

[0021] The second mounting cavity contains a second inclined block that mates with the second centrifugal wedge.

[0022] Optionally, a second elastic retaining ring for constraining the connecting assembly is installed at one end of the second mounting cavity.

[0023] Optionally, a connecting block is provided at one end of the interior of the second mounting cavity, and a connecting slot is provided at one end of the second plug-in block. The connecting block engages with the connecting slot to achieve circumferential positioning.

[0024] Optionally, a limiting block is installed at one end of the second plug-in block, and one end of the limiting block is fixedly connected to the transmission rod.

[0025] Optionally, a limiting groove is formed on the inner side wall of the NTE sleeve, and a limiting sleeve is installed on the outer side wall of the transmission rod. The outer side wall of the limiting sleeve abuts against the inner side wall of the limiting groove to achieve axial positioning.

[0026] Optionally, the outer side wall of the spindle is symmetrically equipped with end face teeth for providing centering accuracy and torque bearing capacity.

[0027] Compared with the prior art, this application includes at least one of the following beneficial technical effects:

[0028] This invention employs a modular structural design, setting the bearing module, main shaft, impeller mounting cavity, transmission rod, etc., as independent modules. These modules are flexibly connected via plug-in and centrifugal locking structures. When localized failures such as damaged working blades occur, the damaged module can be disassembled and replaced selectively, eliminating the need to replace the entire rotor. This significantly reduces resource waste, lowers spare parts inventory and maintenance costs, and shortens equipment downtime for repairs.

[0029] This invention employs a combination design of centrifugal locking structure and end face teeth. When the rotor rotates at high speed, the centrifugal wedge and inclined block convert centrifugal force into axial compressive force, which, combined with the preload of the end face teeth, increases the contact pressure between modules, effectively suppressing whirl tendency at high speeds and ensuring operational stability.

[0030] This invention uses an NTE sleeve made of a negative thermal expansion material, which expands in volume under cryogenic conditions. Its axial elongation precisely offsets the low-temperature shrinkage of the impeller and shaft section, so that the rotor shaft system always maintains a constant tension state, avoids the failure of preload at low temperatures, and is suitable for operation in a wide temperature range from room temperature to near absolute zero.

[0031] In summary, this invention, through its integrated design of modular plug-in structure, centrifugal locking and end-face tooth coordinated torque transmission, and negative thermal expansion NTE bushing temperature change compensation, not only enables rapid local replacement and maintenance of the rotor, but also significantly improves the operational stability under high-speed conditions and effectively solves the problem of preload failure caused by cold contraction in cryogenic environments. Attached Figure Description

[0032] Figure 1 This is a schematic diagram of the main structure of the present invention;

[0033] Figure 2 This is a first-view structural diagram of the disassembled parts of the first plug-in block, the first mounting cavity, and the second plug-in block in this invention;

[0034] Figure 3This is a second-view structural diagram of the disassembled parts of the first plug-in block, the first mounting cavity, and the second plug-in block in this invention;

[0035] Figure 4 This is a schematic diagram of the combined component structure of the second insertion block, the limiting block, and the transmission rod in this invention;

[0036] Figure 5 This is a cross-sectional structural diagram of the NTE sleeve and the enlarged cavity in this invention.

[0037] Reference numerals: 1. Bearing module; 2. Main shaft; 3. End face tooth; 4. First insertion block; 5. First centrifugal wedge; 6. First mounting cavity; 7. First inclined block; 8. Snap-fit ​​block; 9. Snap-fit ​​groove; 10. First elastic retaining ring; 11. Power blade; 12. Second mounting cavity; 13. Second elastic retaining ring; 14. Second inclined block; 15. Connecting snap-fit ​​block; 16. Second insertion block; 17. Connecting snap-fit ​​groove; 18. Second centrifugal wedge; 19. Limiting block; 20. Transmission rod; 21. Limiting sleeve; 22. NTE sleeve; 23. Enlarged cavity; 24. Limiting groove. Detailed Implementation

[0038] The following specific examples illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that, unless otherwise specified, the following embodiments and features described therein can be combined with each other.

[0039] Example: Figure 1 As shown, the present invention proposes a modular rotor assembly for a turbine expander, including a bearing module 1, which is a gas bearing structure. The bearing module 1 is fixedly connected to the outer wall of the middle end of the main shaft 2. The main shaft 2 is made of high-strength precipitation-hardening stainless steel. The outer wall of the main shaft 2 is symmetrically fixedly connected with end face teeth 3 (Hirth teeth) around the bearing module 1. Both ends of the main shaft 2 are fixedly connected with connecting components, which include a first insertion block 4 and a first centrifugal wedge 5. Both ends of the main shaft 2 are fixedly connected with the first insertion block 4. The outer wall of the first insertion block 4 is fixedly connected with the first centrifugal wedge 5 at equal intervals. The end of the first insertion block 4 away from the main shaft 2 is provided with a snap-fit ​​groove 9. The inner wall of the snap-fit ​​groove 9 is set with a gear-shaped structure.

[0040] During use, the end face teeth 3 provide extremely high centering accuracy and torque bearing capacity. When connecting the expansion impeller structure composed of several working blades 11, the traditional bolt connection method is abandoned and a faster connection method is adopted, thereby realizing the modularity of this device. In subsequent use, targeted replacements can be made and timely adjustments can be made, avoiding the drawbacks of overall replacement.

[0041] Reference Figures 1-4 Both ends of the main shaft 2 are connected to the first mounting cavity 6 via connecting components. The first mounting cavity 6 has a hollow first inclined block 7 fixedly connected inside. The inner sidewall of the first inclined block 7 is in contact with the outer sidewall of the first centrifugal wedge 5. The middle of the first mounting cavity 6 has a snap-fit ​​block 8 that matches the size of the inner sidewall of the snap-fit ​​groove 9. The outer wall of one end of the first mounting cavity 6 is fixedly connected to a first elastic retaining ring 10. The end of the first mounting cavity 6 away from the main shaft 2 is fixedly connected to a second mounting cavity 12. The outer wall of the second mounting cavity 12 is fixedly connected with several working blades 11 at equal intervals. The working blades 11 are milled from 7075 aluminum alloy. The several working blades 11 form an expansion impeller structure.

[0042] An expansion impeller structure is formed by several working blades 11. High-pressure gas enters the impeller and expands within the blade flow channel, converting the gas's pressure and thermal energy into the mechanical energy of the rotor's rotation. The airflow also performs work on the blades, directly driving the main shaft 2 to rotate at high speed, providing power to the rear braking end. Simultaneously, the main shaft 2 is inserted into the second mounting cavity 12 via the first insertion block 4 in the connecting assembly. This causes the outer wall of the first centrifugal wedge 5 on the outer wall of the first insertion block 4 to contact the first inclined block 7 fixed inside the first mounting cavity 6. When the device is stationary... The first elastic retaining ring 10 constrains the connecting assembly. When the device is in operation, the centrifugal force on the first centrifugal wedge 5 moves outward, causing the first inclined block 7 to interact with the first centrifugal wedge 5. According to the wedge principle, the radial displacement is efficiently converted into axial compressive force. This compressive force is superimposed on the preload of the central tie rod, which improves the convenience of later maintenance. Furthermore, when the first plug-in block 4 and the first mounting cavity 6 are connected, the snap-fit ​​block 8 and the snap-fit ​​groove 9 snap into each other, which further improves the stability of the connection and effectively ensures the stability of the device operation.

[0043] Reference Figures 1-4A second elastic retaining ring 13 is fixedly connected to the end of the second mounting cavity 12 away from the first mounting cavity 6. A second inclined block 14 is fixedly connected to the inner wall of the second mounting cavity 12. The second inclined block 14 is hollow. A connecting block 15 is fixedly connected to the middle of the second mounting cavity 12. Second insertion blocks 16 are inserted and installed inside the second mounting cavity 12. A gear-shaped connecting groove 17 is opened inside one end of the second insertion block 16. The inner wall size of the connecting groove 17 is adapted to the outer wall size of the connecting block 15. Second centrifugal wedges 18 are fixedly connected at equal intervals to the outer wall of the second insertion block 16. The outer wall of the second centrifugal wedge 18 is in contact with the inner wall of the second inclined block 14. The inclined angle of the first inclined block 7 is between 22.5° and 2.5°. The first centrifugal wedge 5 is made of high-density tungsten alloy and has a weight between 5g and 15g.

[0044] The second mounting cavity 12 is connected to the transmission rod 20 by inserting the second insertion block 16 inside the second mounting cavity 12. The transmission rod 20 then connects to the main shaft 2 and the first mounting cavity 6, forming a modular structure that allows for targeted replacement of necessary components. Simultaneously, after the second insertion block 16 is inserted into the second mounting cavity 12, the outer wall of the second centrifugal wedge 18 contacts the second inclined block 14 fixed inside the second mounting cavity 12. When the device is stationary, the second elastic retaining ring 13 constrains the second insertion block 16 and the second centrifugal wedge 18. When the device is in operation, the second insertion block 16 and the centrifugal force it receives move outward, thereby causing the second inclined block 14 to interact with the second insertion block 16. According to the wedge principle, the radial displacement is efficiently converted into axial compressive force. At the same time, after the second insertion block 16 is inserted into the second mounting cavity 12, the connecting block 15 will be engaged with the inside of the connecting slot 17, thereby effectively improving the stability between transmissions. The second centrifugal wedge 18 is made of high-density tungsten alloy and has a mass between 3g and 10g. The inclination angle of the second inclined block 14 is between 22.5° and 2.5°.

[0045] Reference Figure 1 and Figure 5 The second insertion block 16 is fixedly connected to one end of the limiting block 19, and the other end of the limiting block 19 is fixedly connected to a transmission rod 20. The transmission rod 20 passes through the interior of the NTE sleeve 22. The NTE sleeve 22 is made of a negative thermal expansion material. A limiting groove 24 is formed on the inner wall of one end of the NTE sleeve 22. The inner side wall of the limiting groove 24 abuts against the outer side wall of the limiting sleeve 21. The limiting sleeve 21 is fitted onto the outer side wall of the transmission rod 20. An enlarged cavity 23 is integrally formed in the middle of the NTE sleeve 22. The linear expansion coefficient of the NTE sleeve 22 should be within −5×10. −6 / K to −10×10 −6 Between / K.

[0046] The above structure, through the NTE sleeve 22, allows for low-speed cryogenic operation. Due to the exceptional thermodynamic properties of the NTE sleeve 22 and the expansion cavity 23, their molecular lattice structure undergoes specific torsion as the temperature decreases, resulting in macroscopic volume expansion. This allows the axial elongation at low temperatures to precisely offset the shrinkage of the impeller and shaft section, ensuring that the main shaft 2 and the transmission rod 20 remain under constant tension, thus preventing preload failure. Furthermore, the transmission rod 20 is connected to the NTE sleeve 22 via the limiting sleeve 21 and the limiting block 19. Specifically, the outer wall of the limiting sleeve 21 abuts against the limiting groove 24 opened on the inner wall of the NTE sleeve 22 for limiting, while one end of the outer wall of the limiting block 19 abuts against one end of the outer wall of the NTE sleeve 22.

[0047] The centrifugal locking structure formed by the first centrifugal wedge 5 and the first inclined block 7, and the centrifugal locking structure formed by the second centrifugal wedge 18 and the second inclined block 14, when the device enters the high-speed rotation stage, the first centrifugal wedge 5 and the second centrifugal wedge 18 are thrown outwards, with a centrifugal force of The axial force after the wedge transformation ,in This represents the centrifugal force acting on the centrifugal wedge. This is expressed as the mass of the first centrifugal wedge 5. It is expressed as the angular velocity of the entire device when it rotates at high speed. This is expressed as the radius of rotation from the centrifugal wedge's center of mass to the axis of rotation. It is represented as the axial locking force generated after the centrifugal force is converted by the inclined plane, where θ is the angle of the inclined plane. In this way, the axial force acts directly on the end face tooth 3, thus increasing the contact pressure by 20%-35% and effectively suppressing the tendency of the shaft to whirl at high speed.

[0048] The implementation principle of a modular rotor assembly for a turbine expander according to an embodiment of the present invention is as follows:

[0049] First, the various structures are assembled and connected. Specifically, the first plug-in blocks 4 at both ends of the main shaft 2 are inserted into the first mounting cavity 6, so that the first centrifugal wedge block 5 and the first inclined block 7 fit tightly together. The snap-fit ​​block 8 and the snap-fit ​​groove 9 are snapped together to achieve circumferential positioning. The first elastic retaining ring 10 completes the component constraint in the static state. Then, the second plug-in block 16 is inserted into the second mounting cavity 12, so that the second centrifugal wedge block 18 and the second inclined block 14 fit together. The connecting snap-fit ​​block 15 and the connecting snap-fit ​​groove 17 are snapped together for positioning. The second elastic retaining ring 13 completes the constraint between the impeller module and the transmission rod 20. Finally, the NTE sleeve 22 is fitted on the outside of the transmission rod 20. The positioning of the transmission rod 20 and the NTE sleeve 22 is achieved by the contact between the limiting sleeve 21 and the limiting groove 24. The end face teeth 3 provide the initial centering and pre-tightening foundation for the splicing of each module, thus completing the modular assembly of the entire rotor assembly.

[0050] Subsequently, during operation, the high-pressure gas impacts the working blades 11 on the outside of the second mounting cavity 12. The gas expands adiabatically within the blade flow channel, converting its own pressure energy and thermal energy into mechanical energy. This drives the impeller to rotate the first mounting cavity 6 and the main shaft 2 at high speed. The rotational torque of the main shaft 2 is efficiently transmitted to the two end modules through the end face teeth 3 and the contact surface of the centrifugal locking structure, and then transmitted to the rear braking end through the transmission rod 20. This achieves energy recovery. At the same time, the internal energy of the gas is greatly reduced due to expansion, thus completing the core cooling function of the turbine expander.

[0051] Then, when the rotor rotates at high speed, the first centrifugal wedge 5 and the second centrifugal wedge 18 are thrown outward by centrifugal force, and generate radial displacement along the first inclined block 7 and the second inclined block 14. According to the wedge principle, the radial centrifugal force is converted into axial compressive force, which is superimposed with the pre-tightening force of the end face teeth 3, thereby increasing the contact pressure between modules, suppressing the whirling of the main shaft 2, and the higher the speed, the greater the locking force, thus achieving self-reinforcing anti-loosening and stable torque transmission.

[0052] Furthermore, under cryogenic conditions, metal components such as the main shaft 2 and transmission rod 20 undergo low-temperature shrinkage, while the NTE sleeve 22, made of negative thermal expansion material, expands in volume as the temperature decreases. Its axial elongation precisely offsets the shrinkage of the shaft system and impeller module. Through the cooperation of the limiting sleeve 21 and the limiting groove 24, the rotor shaft system is kept in a constant tension state, avoiding the failure of preload at low temperatures and ensuring the sealing gap and module connection accuracy.

[0053] Finally, the gear-shaped locking structure of the locking block 8 and the locking groove 9, as well as the connecting locking block 15 and the connecting groove 17, effectively restricts the relative circumferential rotation between modules. Combined with the meshing of the end face teeth 3, it further improves the stability of torque transmission at high speeds and ensures the running accuracy of the entire rotor assembly. Thus, the modular rotor assembly of the turbine expander is completed.

[0054] It is worth noting that this invention abandons the integrated structure of traditional turbine expander rotors, designing the bearing module 1, main shaft 2, impeller mounting cavities (i.e., the first mounting cavity 6 and the second mounting cavity 12), and transmission rod 20 as independent modular units. The modules are flexibly connected through plug-in and centrifugal locking structures, eliminating the need for traditional bolted connections or integral forging methods. When localized failures occur, such as damage to the working blades 11 or seal wear, operators can selectively disassemble and replace the damaged module without scrapping the entire rotor. This design effectively solves the technical problem of requiring complete replacement of the entire rotor for localized failures in traditional integral rotors, significantly reducing the waste of precious metal materials, decreasing the types and quantities of spare parts, significantly saving on subsequent maintenance costs, and greatly shortening equipment downtime for repairs, thus improving the operational economy and maintenance convenience of the equipment.

[0055] This invention employs a combination design of centrifugal locking structure and end face teeth 3. Centrifugal wedges (i.e., the first centrifugal wedge 5 and the second centrifugal wedge 18) at both ends of the main shaft 2, together with inclined blocks (i.e., the first inclined block 7 and the second inclined block 14) inside the mounting cavity, form a self-reinforcing locking structure: when the rotor is stationary, each module is constrained by elastic retaining rings (i.e., the first elastic retaining ring 10 and the second elastic retaining ring 13); when the rotor enters a high-speed rotation state, the centrifugal wedges (the first centrifugal wedge 5 and the second centrifugal wedge 18) are thrown outward by centrifugal force, generating radial displacement along the inclined blocks (the first inclined block 7 and the second inclined block 14). According to the wedge principle, the radial centrifugal force is efficiently converted into axial compressive force. This compressive force, combined with the preload provided by the end face teeth 3, significantly increases the contact pressure between modules by 20%-35%. The end face teeth 3 also provide extremely high centering accuracy and torque bearing capacity, effectively suppressing the whirling tendency of the main shaft 2 at high speeds, ensuring transmission stability and operational reliability under ultra-high-speed rotation conditions.

[0056] This invention employs an NTE sleeve 22 made of a negative thermal expansion material to encase the transmission rod 20. This sleeve possesses exceptional thermodynamic properties: as the operating temperature decreases, its molecular lattice structure undergoes a specific torsion, resulting in macroscopic volume expansion. Under cryogenic conditions, when metal components such as the main shaft 2 and transmission rod 20 experience low-temperature contraction, the axial elongation of the NTE sleeve 22 precisely offsets the shrinkage of the impeller (composed of the second mounting cavity 12 and the working blades 11) and the shaft section. Through the cooperation of the limiting sleeve 21 and the limiting groove 24, the rotor shaft system maintains a constant tension, effectively avoiding the problem of preload failure at low temperatures in traditional structures. This design allows the rotor assembly to perfectly adapt to a wide temperature range from room temperature to near absolute zero, ensuring the stability of the sealing gap and module connection accuracy throughout the entire operating temperature range.

[0057] The above specific embodiments are merely several optional embodiments of the present invention. Based on the technical solutions of the present invention and the relevant teachings of the above embodiments, those skilled in the art can make various alternative improvements and combinations to the above specific embodiments.

Claims

1. A modular rotor assembly for a turbine expander, characterized in that, include: Bearing module (1), wherein a main shaft (2) is installed through the interior of the bearing module (1); Both ends of the main shaft (2) are detachably connected to the first mounting cavity (6) via a connecting assembly; A second mounting cavity (12) is installed on the outer wall of one end of the first mounting cavity (6), and power blades (11) are installed at equal intervals on the outer wall of the second mounting cavity (12). One end of the transmission rod (20) is detachably inserted into the interior of the second mounting cavity (12) via a connecting assembly; The transmission rod (20) is fitted with an NTE sleeve (22), which is made of a negative thermal expansion material.

2. The modular rotor assembly for a turbine expander according to claim 1, characterized in that, The connection component includes: The first connector (4) is installed at the end of the main shaft (2); Multiple first centrifugal wedges (5) are installed at equal intervals on the outer side wall of the first plug-in block (4); The first mounting cavity (6) is equipped with a first inclined block (7) that cooperates with the first centrifugal wedge (5).

3. A modular rotor assembly for a turbine expander according to claim 2, characterized in that, A first elastic retaining ring (10) for constraining the connecting assembly is installed on the outer wall of one end of the first mounting cavity (6).

4. A modular rotor assembly for a turbine expander according to claim 2, characterized in that, The first mounting cavity (6) has a snap-fit ​​block (8) at one end, and the first insertion block (4) has a snap-fit ​​groove (9) at the end away from the main shaft (2). The snap-fit ​​block (8) and the snap-fit ​​groove (9) are snap-fitted together to achieve circumferential positioning.

5. A modular rotor assembly for a turbine expander according to claim 1, characterized in that, The connecting components include: The second plug-in block (16) is plugged into the interior of the second mounting cavity (12); Multiple second centrifugal wedges (18) are installed at equal intervals on the outer side wall of the second plug-in block (16); The second mounting cavity (12) is equipped with a second inclined block (14) that cooperates with the second centrifugal wedge (18).

6. A modular rotor assembly for a turbine expander according to claim 5, characterized in that, A second elastic retaining ring (13) for constraining the connecting assembly is installed at one end of the second mounting cavity (12).

7. A modular rotor assembly for a turbine expander according to claim 5, characterized in that, The second mounting cavity (12) has a connecting block (15) at one end and a connecting slot (17) at one end of the second plug-in block (16). The connecting block (15) and the connecting slot (17) engage to achieve circumferential positioning.

8. A modular rotor assembly for a turbine expander according to claim 5, characterized in that, A limiting block (19) is installed at one end of the second plug-in block (16), and one end of the limiting block (19) is fixedly connected to the transmission rod (20).

9. A modular rotor assembly for a turbine expander according to claim 1, characterized in that, The inner wall of the NTE sleeve (22) is provided with a limiting groove (24), and the outer wall of the transmission rod (20) is provided with a limiting sleeve (21). The outer wall of the limiting sleeve (21) abuts against the inner wall of the limiting groove (24) to achieve axial positioning.

10. A modular rotor assembly for a turbine expander according to claim 1, characterized in that, The outer side wall of the spindle (2) is symmetrically equipped with end face teeth (3) for providing centering accuracy and torque bearing capacity.

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