Modular combined centrifugal compressor for high pressure ratio high temperature heat pumps

Abstract

The application discloses a modular combined centrifugal compressor for high-pressure ratio high-temperature heat pumps, which adopts a double-shaft extension motor structure and comprises an IGV capacity adjusting mechanism device and a volute assembly. Optionally, a gear box assembly can be arranged when the impeller is speed-increased, and the gear box assembly is not arranged when the compressor is directly assembled on the motor shaft. The volute of the volute assembly is a central symmetrical structure, and the left and right sides can be directly translated and interchanged, thereby reducing the types of spare parts. The IGV capacity adjusting mechanism device comprises multiple driven gears, a first tooth ring, a second tooth ring and a floating mounting base. The blades are connected with the driven gears, the first tooth ring is matched with the second tooth ring to form double-tooth ring synchronous driving of all the driven gears, and the blades, the second tooth ring and the driven gears are all arranged on the floating mounting base. The floating mounting base moves in the axial direction of the air flow thrust, and self-adaptingly compensates the meshing gap. Through the floating self-adapting transmission and the central symmetrical modular structure, the compressor can keep stable and reliable on-line blade adjusting capacity under high-temperature variable working conditions.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a modular combined centrifugal compressor for high-pressure, high-temperature heat pumps. Background Technology

[0002] Among the high-temperature heat pumps on the market with temperatures ranging from 100 to 150°C, centrifugal compressors are typically selected for large-capacity applications, such as cocoa oil refining, textiles, papermaking, pharmaceutical intervention, alcohol refining, and general equipment manufacturing. Cascade ultra-high temperature centrifugal heat pump units with bromine-electric coupling systems have competitive advantages in terms of high efficiency and stable operation.

[0003] A centrifugal compressor mainly consists of the following modules: an impeller, the core component that powers the compressor, which transfers mechanical energy to the gas through high-speed rotation, increasing its pressure and velocity; a main motor assembly, which drives the impeller and typically uses an asynchronous low-speed motor or a permanent magnet synchronous high-speed motor; an IGV (Inlet Gas Ventilation) capacity regulating mechanism, located in front of the impeller, which is an annular channel with a gradually increasing flow area, designed to evenly draw gas into the compressor; and a volute assembly, including the volute casing: the main pneumatic assembly of the centrifugal compressor head, where refrigerant gas is evenly drawn into the centrifugal impeller through the IGV mechanism. Under the centrifugal force of high-speed rotation, the refrigerant gas is compressed and pressurized, then further diffused in the diffuser and guided to the exhaust port. In some compressor designs, a gearbox assembly is added between the impeller and the main motor assembly to increase transmission speed and improve efficiency, while also allowing for flexible adjustment of the impeller speed to adapt to different operating conditions.

[0004] Regarding the aforementioned technologies, in centrifugal compressors, the IGV capacity regulation mechanism includes a housing and blades arranged circumferentially inside the housing. It primarily adjusts the airflow angle and flow area by changing the blade angle, thereby adapting to varying compressor operating conditions, improving efficiency, and effectively delaying surge at low flow rates. To maintain continuous production and achieve real-time anti-surge protection, the adjustment of these blades is typically completed online while the compressor is running. This places extremely high demands on the reliability of the regulation mechanism under high temperature, high pressure, oil-free conditions, and airflow pulsation.

[0005] Synchronous adjustment of the blades in the IGV capacity regulating mechanism can be achieved using a gear and ring drive mechanism. A large gear ring simultaneously drives multiple small gears mounted on the ends of each blade shaft, enabling multi-blade linkage. However, conventional rigid gear and ring solutions face a series of challenges in the harsh environment inside the compressor: the thermal expansion difference between the casing and the gear ring causes drastic changes in the meshing clearance between hot and cold states; too small a clearance may cause jamming, while too large a clearance leads to transmission backlash and blade vibration; after normal wear of the meshing surfaces during long-term operation, the fixed structure cannot compensate online, resulting in a gradual decrease in accuracy; airflow vibration is directly transmitted to the gear pair, causing tooth surface knocking and fretting fatigue; and the simultaneous driving of several small gears by the gear ring requires extremely high machining and assembly precision, with accumulated errors easily leading to inconsistent blade rotation angles and blade detuning.

[0006] In addition, the existing dual-shaft compressors have poor interchangeability of left and right side body components and internal parts, resulting in a wide variety of parts, a large demand for spare parts, and poor maintenance economy. Summary of the Invention

[0007] To address the aforementioned problems, this application provides a modular, combined centrifugal compressor for high-pressure, high-temperature heat pumps.

[0008] This application provides a modular, combined centrifugal compressor for high-pressure, high-temperature heat pumps, employing the following technical solution: A modular combined high-pressure ratio high-temperature heat pump centrifugal compressor adopts a dual-shaft extension drive structure, which is directly or indirectly connected to the impeller through a gearbox assembly. It also includes an IGV capacity adjustment mechanism and a worm gear assembly located behind the IGV capacity adjustment mechanism. The volute in the volute assembly has a centrally symmetrical structure, which allows the volute assemblies on both sides of the compressor to be interchanged. The IGV capacity regulation mechanism includes: Multiple driven gears are used to connect to the shaft ends of each blade in the IGV capacity adjustment mechanism. The first gear ring and the second gear ring, each driven gear simultaneously meshing with the first gear ring and the second gear ring; The first gear ring is configured to rotate by receiving torque from an external drive source and drive the second gear ring to rotate synchronously via a driven gear; The floating mount includes a mounting ring, a clamping ring, and a collar. The driven gear has a rotating shaft. The mounting ring and the clamping ring are arranged along the axial direction and are detachably connected to each other. There is a movable gap between the mounting ring and the housing. A receiving cavity is formed on the side of the clamping ring and the mounting ring that are close to each other. The collar is located in the receiving cavity. The rotating shaft of the driven gear passes through the collar and is connected to the blade. The second tooth rotates around its own axis and is rotatably connected to the mounting ring. Under the thrust generated by the airflow acting on the blade, the floating mount moves relative to the housing along the axial direction of the second tooth ring to adaptively compensate for the meshing clearance.

[0009] By adopting the above technical solution, the centrally symmetrical volute allows for interchangeable installation of the volute assemblies on both sides of the compressor, reducing the types of parts, lowering spare parts inventory costs, and simplifying maintenance. The dual-ring synchronous drive system, consisting of multiple driven gears, a first ring gear, and a second ring gear, can evenly distribute torque to each blade, improving the consistency and adjustment accuracy of blade angles. The floating mount adopts a separate, detachable structure consisting of a mounting ring, a clamping ring, and a collar, facilitating independent assembly, disassembly, and maintenance of the driven gears. The movable clearance between the mounting ring and the housing provides the motion basis for the overall movement of the floating mount. The thrust of the airflow acting on the blades is effectively utilized, driving the floating mount to move the driven gears and the second ring gear along the axial direction. During operation, it adaptively compensates for changes in meshing clearance, reducing the risk of jamming, minimizing transmission backlash, and improving adjustment reliability under varying operating conditions.

[0010] Optionally, it also includes: an elastic element 1, which is disposed between the floating mount and the housing, for applying a basic preload force to the floating mount in the direction of the first toothed ring.

[0011] By adopting the above technical solution, the addition of the elastic element can provide a basic preload in the direction of the first gear ring when the airflow thrust is insufficient, maintain the meshing state between the driven gear and the first gear ring, avoid excessive clearance causing blade vibration or adjustment failure, and broaden the effective working condition range of adaptive compensation.

[0012] Optionally, a dry friction damping structure is provided at the guide mating surface between the floating mounting base and the housing.

[0013] By adopting the above technical solution, the dry friction damping structure can dissipate the vibration energy of the floating mounting seat under airflow pulsation, suppress tooth surface knocking and fretting wear, and improve the smoothness and durability of the transmission chain under long-term online adjustment.

[0014] Optionally, a thermal compensation washer is provided between the back of the first gear ring and the housing. The thermal compensation washer is made of bimetallic or shape memory alloy and is used to generate axial and / or radial deformation when the temperature changes, so as to compensate for the change in meshing clearance between the driven gear and the first gear ring caused by thermal expansion.

[0015] By adopting the above technical solution, the thermal compensation washer ring is made of bimetallic or shape memory alloy. It can actively compensate for the change in meshing clearance caused by thermal expansion by utilizing the axial and / or radial deformation of the material when the temperature changes, thereby reducing the risk of jamming caused by too small a clearance or the impact noise caused by too large a clearance.

[0016] Optionally, it also includes a stop portion, which is fixed to the housing of the IGV capacity adjustment mechanism device to limit the axial range of motion of the floating mounting base.

[0017] By adopting the above technical solution, the stop part can limit the axial movement range of the floating mounting seat, prevent the transmission chain from disengaging or interfering due to overtravel under extreme working conditions, and provide a safety boundary for the axial floating adaptive function.

[0018] Optionally, an axial deformation floating gap is provided between the second toothed ring and the floating mounting seat. The floating mounting seat is provided with rollers for supporting the rotation of the second toothed ring. An elastic element two is provided between the floating mounting seat and the second toothed ring. The elastic element two applies a preload thrust to the second toothed ring to move it closer to the driven gear, so that the second toothed ring and the driven gear remain engaged.

[0019] By adopting the above technical solution, the axial deformation floating clearance, rollers and elastic element II are set so that the second gear ring can independently follow the slight axial displacement of the driven gear and maintain close meshing. It forms a graded response with the overall axial floating of the floating mounting seat, improves the balance of multi-point meshing, and reduces local off-center load or interference caused by inconsistent clearance on both sides.

[0020] Optionally, it also includes: a limiting ring, which is located outside all driven gears and connected to the IGV capacity adjustment mechanism. The limiting ring has several support covers on the side facing the driven gear. The support covers are slidably connected to the limiting ring along the driven gear axis. An elastic unit three is provided between the limiting ring and the support covers. The elastic unit three applies a thrust to the support covers toward the blades. A support shaft is coaxially fixed on the side of the driven gear away from the blades. The end of the support shaft away from the driven gear abuts against the support cover and rotates under the support of the support cover.

[0021] By adopting the above technical solution, the combination of the limiting ring, the support cover and the elastic unit can provide axial support to the driven gear from the outside, effectively restricting its axial movement. The support shaft rotates under the support of the support cover, keeping the meshing position of the gear and the gear ring stable, so that the axial floating function of the floating mounting seat and the axial positioning of the driven gear do not interfere with each other.

[0022] Optionally, it also includes: a transmission plate, an arc-shaped opening is provided on the outer side of the IGV capacity adjustment mechanism, the transmission plate is located in the arc-shaped opening and slides along the arc-shaped opening, the IGV capacity adjustment mechanism is provided with a transmission rod for pushing the transmission plate to move along the arc-shaped opening, the transmission rod is connected to an external drive source, the transmission plate is located outside the first toothed ring, and a plurality of transmission grooves are provided on the side of the transmission plate facing the first toothed ring along the axial direction, a transmission block adapted to the transmission groove is fixedly connected to the outer circle of the first toothed ring, the transmission block is located in the transmission groove and fits against the inner wall of the transmission groove, when the transmission plate moves along the arc-shaped opening, the first toothed ring is driven to rotate circumferentially through the cooperation of the transmission block and the transmission groove, and the first toothed ring and the transmission block have an axial clearance.

[0023] By adopting the above technical solution, the arc-shaped opening provides a sliding guide for the transmission plate, the transmission rod is connected to the external drive source to provide driving force, and the cooperation of the transmission plate, transmission groove and transmission block realizes torque transmission. The axial movement gap between the first toothed ring and the transmission block allows the first toothed ring to generate axial micro-movement due to thermal expansion while transmitting torque, avoiding additional stress and jamming, and making the drive interface adapt to the relative displacement caused by the axial floating of the floating mounting seat.

[0024] In summary, this application includes at least one of the following beneficial technical effects: 1. By mounting the blades, driven gear, and second gear ring together on an axially floating mounting base, and utilizing the thrust generated by the airflow acting on the blades to drive the floating mounting base to move, the transmission system can automatically and in real time compensate for changes in meshing clearance caused by thermal expansion and wear during compressor operation. When the temperature rises and the clearance decreases, the floating mounting base can retract to prevent jamming; when the temperature drops or the tooth surface wears and the clearance increases, the floating mounting base can advance to reduce hysteresis. This adaptive mechanism requires no external control and no downtime for adjustment, solving the fundamental contradiction of traditional rigid fixed structures in achieving adequate clearance under variable temperature conditions. 2. The first and second gear rings simultaneously mesh with each driven gear, and the first gear ring receives external torque to drive all driven gears to rotate synchronously. The double gear rings evenly distribute the driving force, avoiding the problems of uneven load and inconsistent blade angles that may occur with single-point drive by a single gear ring. On this basis, the floating mounting base undertakes the clearance compensation function, and the double gear ring structure ensures that all driven gears remain synchronously linked during the compensation process, so that the blade adjustment mechanism has self-adaptive capability without sacrificing adjustment accuracy; 3. The volute assembly's casing is designed with a centrally symmetrical structure, allowing the left and right sides of the volute assembly to be interchangeably installed. This improvement directly reduces the types of compressor parts and the number of spare parts required. In industrial applications such as high-temperature heat pumps that require long-term continuous operation, this effectively reduces user maintenance costs and downtime for repairs, while improving the overall modularity and economy of the machine. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the overall structure of Example 1.

[0026] Figure 2 This is a schematic diagram designed to highlight the external structure of the IGV capacity regulation mechanism.

[0027] Figure 3 This is a schematic diagram designed to highlight the internal structure of the IGV capacity regulation mechanism.

[0028] Figure 4 This is a schematic diagram designed to highlight the external structure of the floating mount.

[0029] Figure 5 yes Figure 3 An enlarged schematic diagram of part A in the middle.

[0030] Figure 6 yes Figure 3 Enlarged diagram of part B.

[0031] Figure 7 This is a schematic diagram of the overall structure of Example 2.

[0032] Explanation of reference numerals in the attached drawings: 1. IGV capacity adjustment mechanism; 11. Housing; 111. Assembly ring; 112. Positioning bolt; 113. Arc-shaped opening; 114. Annular groove; 115. Guide ring; 116. Sealing shell; 117. Positioning groove; 12. Blade; 2. Worm gear assembly; 31. Driven gear; 311. Rotating shaft; 312. Support shaft; 32. First gear ring; 321. Transmission block; 33. Second gear ring; 34. Floating mounting base; 341. Mounting ring; 3411. Positioning protrusion; 34 2. Clamping ring; 343. Collar; 35. Elastic element one; 36. Dry friction damping structure; 37. Thermal compensation pad ring; 38. Stop part; 381. Buffer pad; 39. Elastic element two; 391. Roller; 392. Roller; 4. Limiting ring; 41. Half ring one; 42. Half ring two; 43. Positioning hole; 44. Support cover; 45. Elastic unit three; 51. Transmission plate; 511. Transmission groove; 52. Transmission rod; 53. External drive source; 6. Dual-shaft extension power main motor assembly; 7. Gearbox assembly. Detailed Implementation

[0033] The present application will be further described in detail below with reference to all the accompanying drawings.

[0034] This application discloses a modular, combined centrifugal compressor for high-pressure, high-temperature heat pumps. Example 1

[0035] Reference Figure 1 and Figure 2This embodiment discloses a modular combined high-pressure high-temperature heat pump centrifugal compressor, which adopts a dual-shaft extension drive structure. Specifically, it selects a dual-shaft extension main motor assembly 6, and also includes an IGV capacity adjustment mechanism device 1, a worm gear assembly 2 located behind the IGV capacity adjustment mechanism device 1, and a gearbox assembly 7. The IGV capacity adjustment mechanism device 1 includes a housing 11 and blades 12 disposed within the housing 11.

[0036] Reference Figure 1 and Figure 2 The motor shaft of the dual-shaft extension main motor assembly 6 is connected to the input shaft of the gearbox assembly 7. The driven shaft of the gearbox assembly 7 is connected to the impeller. The dual-shaft extension main motor assembly 6 drives the impeller through gear meshing in the gearbox assembly 7. Two sets of impellers are symmetrically arranged on both sides of the dual-shaft extension main motor assembly 6. The IGV capacity adjustment mechanism 1 is located behind the worm gear assembly 2. An adjustable blade drive device is installed inside the IGV capacity adjustment mechanism 1 to synchronously adjust the angle of each blade 12 within the IGV capacity adjustment mechanism 1. During operation, the dual-shaft extension main motor assembly 6 drives the impeller to rotate. External airflow is drawn in from the inlet of the IGV capacity adjustment mechanism 1 and enters the high-speed rotating impeller. The impeller performs work on the gas, giving it kinetic and pressure energy. The pressurized airflow is thrown out from the impeller and enters the diffuser inside the worm gear assembly 2 for further diffusion, and then flows into the exhaust port of the worm gear assembly 2 for discharge. When the compressor needs to adapt to varying operating conditions, the blade 12 angle can be changed to match different flow and pressure requirements.

[0037] Reference Figure 1 and Figure 2 The volute assembly 2 adopts a centrally symmetrical structure both inside and outside the volute, which allows the volute assemblies 2 on the left and right sides of the compressor to be interchangeable. Specifically, the volute assembly 2 parts on one side can be directly moved to the other side to complete the installation without flipping or repositioning, thereby greatly simplifying maintenance operations and reducing the types of parts and the number of spare parts in reserve.

[0038] Reference Figure 1 and Figure 2 In this embodiment, gearbox assemblies 7 of the same series share a single blank casting. During assembly, the gearbox assembly 7 on one side of the dual-shaft extension main motor assembly 6 is rotated 180° and then moved to the other side to complete the assembly. By setting up interchangeable gearbox assemblies 7 on both sides, the IGV capacity adjustment mechanism device 1 is also configured as an interchangeable structure on both sides. This allows not only the worm gear assembly 2 on both sides of the dual-shaft extension main motor assembly 6 to be interchangeable, but also the transmission end structure, including the gearbox assembly 7, to be rotated and installed in a left-right swap. This further expands the scope of modular interchangeability, enabling more core components on both sides to be interchangeable, reducing the types of spare parts and maintenance complexity of the entire machine.

[0039] Reference Figure 2 and Figure 3 The adjustable blade drive device includes multiple driven gears 31, a first gear ring 32, a second gear ring 33, and a floating mounting base 34. Each driven gear 31 is connected to the shaft end of the corresponding blade 12 in the IGV capacity adjustment mechanism device 1, and each driven gear 31 simultaneously meshes with the first gear ring 32 and the second gear ring 33, forming a double gear ring synchronous drive structure.

[0040] Reference Figure 3 and Figure 4 The blade 12, driven gear 31, and second gear ring 33 are mounted together on the floating mounting base 34. The floating mounting base 34 includes a mounting ring 341, a clamping ring 342, and a collar 343. The mounting ring 341 and the clamping ring 342 are arranged along the axial direction and are detachably connected by bolts. The mounting ring 341 and the clamping ring 342 are arranged along the internal airflow direction of the IGV capacity regulating mechanism device 1. A guide ring 115 is fixed at one end of the housing 11 near the external airflow inlet. The mounting ring 341 is sleeved on the outside of the guide ring 115. The guide ring 115 guides and limits the mounting ring 341, so that the floating mounting base 34 floats only along the axial direction.

[0041] Reference Figure 3 and Figure 4 A positioning protrusion 3411 is fixed on the mounting ring 341, and a positioning groove 117 is provided on the housing 11 at the corresponding position. During assembly, the positioning protrusion 3411 is inserted into the positioning groove 117 to restrict the rotation of the mounting ring 341 around its own axis, so that it can only move axially. The clamping ring 342 and the mounting ring 341 together form a receiving cavity on their adjacent sides, and the collar 343 is embedded in the receiving cavity and fixedly limited.

[0042] Reference Figure 3 and Figure 5 The driven gear 31 is provided with a rotating shaft 311, which passes through the inner hole of the collar 343 and is connected to the blade 12. The collar 343 provides rotational support for the rotating shaft 311. At the same time, both the shaft ends of the rotating shaft 311 and the blade 12 are fixed with bosses, which are located in the receiving cavity, so that the clamping ring 342 cooperates with the mounting ring 341 to restrict the axial displacement of the blade 12 and the driven gear 31.

[0043] Reference Figure 3 and Figure 5 An assembly ring 111 is detachably connected to the side of the housing 11 away from the air intake end by bolts. The assembly ring 111 and the housing 11 cooperate to form a space for accommodating the floating mounting seat 34. The first toothed ring 32 is rotatably mounted on the assembly ring 111. Several rollers 392 are provided between the assembly ring 111 and the first toothed ring 32 to reduce friction, so that the first toothed ring 32 can rotate smoothly.

[0044] Reference Figure 3 and Figure 5 An axial deformation floating gap is provided between the second gear ring 33 and the floating mounting base 34. The floating mounting base 34 is provided with rollers 391 for supporting the rotation of the second gear ring 33. An elastic element 39 is also provided between the floating mounting base 34 and the second gear ring 33. The elastic element 39 applies a preload thrust to the second gear ring 33, causing it to move closer to the driven gear 31. When the driven gear 31 undergoes an axial position change due to the overall movement of the floating mounting base 34 or a slight offset of itself, the second gear ring 33 can independently follow the axial offset within the allowable range of the floating gap under the thrust of the elastic element 39, always maintaining close meshing with the driven gear 31.

[0045] Reference Figure 3 and Figure 5 When the compressor is working, the airflow acts on the surface of the blades 12 to generate thrust. This thrust drives the floating mount 34, together with its components, to move relative to the housing 11 along the axial direction of the second gear ring 33. When thermal expansion or tooth wear causes changes in the meshing clearance, the floating mount 34 can adaptively move to compensate for the clearance, reducing the risk of jamming between the first gear ring 32 and the driven gear 31 and the transmission backlash.

[0046] Reference Figure 3 and Figure 5 Furthermore, this embodiment also includes an elastic element 35, specifically a disc spring. An annular groove 114 is formed on the inner side of the housing 11, and the elastic element 35 is installed within the annular groove 114 and sandwiched between the floating mounting base 34 and the housing 11. The elastic element 35 continuously applies a thrust to the floating mounting base 34 in the direction of the first gear ring 32. When the airflow thrust is insufficient, the basic preload provided by the elastic element 35 can maintain the meshing state between the driven gear 31 and the first gear ring 32.

[0047] Reference Figure 3 and Figure 5 Furthermore, a dry friction damping structure 36 is provided at the guide mating surface between the mounting ring 341 and the housing 11. The dry friction damping structure 36 is an annular gasket made of a combination of metal and rubber materials, embedded inside the mounting ring 341 and in contact with the outer circle of the guide ring 115. When the floating mounting seat 34 vibrates slightly due to airflow pulsation, friction occurs between the metal wires inside the metal rubber and between the metal wires and the mating surface, dissipating vibration energy and thus suppressing tooth surface knocking and fretting wear.

[0048] Reference Figure 3 and Figure 5In addition, a thermal compensation washer 37 is provided between the back of the first gear ring 32 and the assembly ring 111. The thermal compensation washer 37 is made of bimetallic or shape memory alloy. When the temperature changes, the thermal compensation washer 37 undergoes axial and / or radial deformation, actively compensating for the change in meshing clearance between the driven gear 31 and the first gear ring 32 caused by thermal expansion.

[0049] Reference Figure 3 and Figure 5 It also includes a stop portion 38, which is located at the end faces of the guide ring 115 and the assembly ring 111 that are close to each other. The floating mounting seat 34 is located between the two stop portions 38, and the two stop portions 38 cooperate to limit the range of motion of the floating mounting seat 34. Each of the stop portions 38 has a buffer pad 381 on the side facing the floating mounting seat 34, which absorbs impact energy while limiting the maximum axial displacement of the floating mounting seat 34, thereby reducing the hard impact of the floating mounting seat 34.

[0050] Reference Figure 3 and Figure 6 It also includes a limiting ring 4, which includes a first half-ring 41 and a second half-ring 42 that are fastened together along the axial direction. The first half-ring 41 and the second half-ring 42 are detachably connected by bolts. Both the first half-ring 41 and the second half-ring 42 have arc-shaped grooves on their adjacent sides, and the two arc-shaped grooves cooperate to form a receiving cavity.

[0051] Reference Figure 3 and Figure 6 The limiting ring 4 is located on the outside of all driven gears 31. A positioning hole 43 is provided on the outer circumferential surface of the limiting ring 4. A positioning bolt 112 is provided on the housing 11, passing through the housing 11 and inserted into the positioning hole 43 to achieve circumferential and radial positioning of the limiting ring 4. A sealing gasket is provided between the positioning bolt 112 and the housing 11 to ensure the sealing effect of the IGV capacity regulating mechanism device 1.

[0052] Reference Figure 3 and Figure 6 A plurality of support covers 44 are provided on the side of the limiting ring 4 facing the driven gear 31. The support covers 44 are located in the receiving cavity and are slidably connected to the limiting ring 4 along the axial direction of the driven gear 31. An elastic unit 35 is disposed between the limiting ring 4 and the support covers 44, applying a thrust to the support covers 44 in the direction of the blade 12. A support shaft 312 is coaxially fixed on the side of the driven gear 31 away from the blade 12. The end of the support shaft 312 away from the driven gear 31 abuts against the support cover 44. The support shaft 312 rotates freely under the support of the support cover 44, and the support cover 44 applies an axial thrust to the support shaft 312, effectively restricting the axial movement of the driven gear 31. It should be noted that a radial clearance is left between the support shaft 312 and the support cover 44 to meet the movement requirements of the driven gear 31 with the floating mounting base 34.

[0053] Reference Figure 3 and Figure 6 It also includes a transmission plate 51, with an arc-shaped opening 113 circumferentially provided on the outside of the housing 11. The transmission plate 51 is located inside the arc-shaped opening 113 and can slide along the arc-shaped opening 113. A sealing shell 116 is detachably connected to the outside of the housing 11 by bolts. The sealing shell 116 is fastened to the outside of the arc-shaped opening 113 and seals the arc-shaped opening 113, thereby ensuring the airtightness of the housing 11.

[0054] Reference Figure 2 and Figure 6 A transmission rod 52 is rotatably connected to a sealing shell 116. One end of the transmission rod 52 passes through the sealing shell 116 and is rotatably connected to the sealing shell 116 via a bearing. The end of the transmission rod 52 located outside the sealing shell 116 is connected to an external drive source 53. A seal is provided between the transmission rod 52 and the sealing shell 116. The transmission rod 52 is used to drive the transmission plate 51 to reciprocate along the arc-shaped opening 113. The external drive source 53 is a motor, and the transmission rod 52 is a worm gear. A worm wheel tooth that meshes with the worm is provided on the outer circle of the transmission plate 51. When the transmission rod 52 rotates, it drives the transmission plate 51 to move along the arc-shaped opening 113 through meshing with the worm gear.

[0055] Reference Figure 2 and Figure 6 The transmission plate 51 is located outside the first gear ring 32, and several transmission grooves 511 are formed along the axial direction on the side of the transmission plate 51 facing the first gear ring 32. A transmission block 321 adapted to the transmission groove 511 is fixedly connected to the outer circle of the first gear ring 32. The transmission block 321 is embedded in the transmission groove 511 and fits against the inner wall of the transmission groove 511. When the transmission rod 52 pushes the transmission plate 51 to move along the arc-shaped opening 113, the first gear ring 32 is driven to rotate circumferentially through the cooperation of the transmission block 321 and the transmission groove 511. There is an axial clearance between the first gear ring 32 and the transmission block 321, which allows the first gear ring 32 to undergo axial micro-movement due to thermal expansion while transmitting torque.

[0056] Reference Figure 2 and Figure 6 When the first gear ring 32 rotates under the action of the transmission plate 51, it drives the second gear ring 33 to rotate synchronously through the driven gear 31, and evenly transmits the driving force to each blade 12, so that all blades 12 rotate synchronously, thereby realizing the adjustment of the blade angle. The tooth surfaces of the first gear ring 32, the second gear ring 33 and the driven gear 31 are all provided with a solid lubricating layer. The solid lubricating layer realizes oil-free lubrication between each meshing pair, so as to adapt to the high temperature environment inside the compressor and avoid lubricating oil contaminating the working fluid. Example 2

[0057] Reference Figure 7 The difference between this embodiment and Embodiment 1 is that the compressor does not have a gearbox assembly 7; instead, the two sets of impellers are directly driven by the dual-shaft extension main motor assembly 6. This design is more compact and has a shorter transmission chain, making it suitable for applications with lower speed regulation requirements or where direct speed control using a variable-speed motor is used. The remaining structure is the same as in Embodiment 1 and will not be described again here.

[0058] The implementation principle of the modular combined high-pressure high-temperature heat pump centrifugal compressor of this application is as follows: When the angle of the blade 12 needs to be adjusted, the external drive source 53 drives the transmission rod 52 to rotate. The transmission rod 52 meshes with the transmission plate 51 through the worm gear teeth, pushing the transmission plate 51 to slide smoothly along the arc-shaped opening 113 on the housing 11. The circumferential movement of the transmission plate 51 is converted into the rotation of the first gear ring 32 through the cooperation of the transmission groove 511 and the transmission block 321, and the torque is thus input into the transmission system. The first gear ring 32 meshes with all driven gears 31 at the same time, and transmits the rotational motion evenly to each driven gear 31, thereby driving the second gear ring 33 to rotate synchronously, and finally driving each blade 12 to rotate synchronously around its own axis to the target angle, so as to achieve precise adjustment of the airflow angle and flow area.

[0059] During continuous operation of the compressor, the transmission system is inevitably affected by temperature and wear. When the internal temperature rises, the difference in thermal expansion between different components causes the meshing clearance to tend to decrease. At this time, under the combined action of thermal stress, the floating mounting base 34 can retract axially, driving the driven gear 31 and the second gear ring 33 to move slightly as a whole, avoiding jamming due to excessive clearance. When the temperature drops or normal wear of the tooth surface causes the clearance to increase, the elastic element 35 located between the floating mounting base 34 and the housing 11 provides a continuous basic preload force, actively pushing the floating mounting base 34 back to its original position, compensating for the clearance to a reasonable range. In this process, the thrust of the airflow acting on the blades 12 also becomes the power source for driving the movement of the floating mounting base 34. Working in conjunction with the elastic force, passive adaptive compensation is achieved, enabling the transmission chain to maintain a suitable meshing state under all operating conditions.

[0060] Furthermore, the dry friction damping structure 36 rapidly dissipates energy through internal friction of the metal rubber when the floating mounting base 34 experiences slight vibrations, suppressing tooth surface knocking and fretting wear. The thermal compensation pad ring 37 actively compensates for thermal deformation from the first toothed ring 32 side, further stabilizing the meshing clearance. The stop part 38 provides a reliable travel boundary for the floating mounting base 34, preventing it from overtraveling. Under the independent preload thrust of the elastic element 39, the second toothed ring 33 can follow the driven gear 31 with slight offset, effectively constraining the axial movement of the driven gear 31 in conjunction with the limit ring 4 and the support cover 44, ensuring the balance of multi-point meshing and the positioning rigidity of the transmission chain. The solid lubricating layer on the surfaces of each meshing pair allows the entire transmission system to operate smoothly in the high-temperature, oil-free environment inside the compressor, while also preventing lubricating oil from contaminating the working fluid.

[0061] Finally, the centrally symmetrical volute and the rotatable and interchangeable gearbox assembly 7 work together to enable the core components on both sides of the compressor to achieve a high degree of modularity and versatility, and maintain stable transmission performance and reliable adjustable blade 12 adjustment capability during long-term operation under varying temperatures and operating conditions.

[0062] The above are all preferred embodiments of this application, and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. A modular combined high-pressure high-temperature heat pump centrifugal compressor, employing a dual-shaft extension drive structure, wherein the dual-shaft extension drive structure is directly or indirectly connected to the impeller via a gearbox assembly (7), and further comprising an IGV capacity regulating mechanism (1) and a worm gear assembly (2) located behind the IGV capacity regulating mechanism (1), characterized in that: The volute in the volute assembly (2) has a centrally symmetrical structure, which allows the volute assemblies (2) on both sides of the compressor to be interchanged. IGV capacity regulation mechanism device (1) includes: Multiple driven gears (31) are used to connect to the shaft ends of each blade (12) in the IGV capacity adjustment mechanism (1); The first gear ring (32) and the second gear ring (33) are connected, and each driven gear (31) simultaneously meshes with the first gear ring (32) and the second gear ring (33); The first gear ring (32) is configured to receive the torque of an external drive source (53) and rotate, and drive the second gear ring (33) to rotate synchronously via the driven gear (31); The floating mounting base (34) includes a mounting ring (341), a clamping ring (342), and a collar (343). The driven gear (31) is provided with a rotating shaft (311). The mounting ring (341) and the clamping ring (342) are arranged along the axial direction and are detachably connected to each other. There is a movable gap between the mounting ring (341) and the housing (11). A receiving cavity is formed on the side of the clamping ring (342) and the mounting ring (341) that are close to each other. The collar (343) is located in the receiving cavity. The rotating shaft (311) of the driven gear (31) passes through the collar (343) and is connected to the blade (12). The second toothed ring (33) is rotatably connected to the mounting ring (341) around its own axis. Under the thrust generated by the airflow acting on the blade (12), the floating mounting base (34) moves along the axial direction of the second toothed ring (33) relative to the housing (11) to adaptively compensate for the meshing gap.

2. The modular combined high-pressure high-temperature heat pump centrifugal compressor according to claim 1, characterized in that, Also includes: Elastic element 1 (35) is disposed between the floating mount (34) and the housing (11) to apply a basic preload force to the floating mount (34) in the direction of the first toothed ring (32).

3. A modular combined high-pressure high-temperature heat pump centrifugal compressor according to claim 1, characterized in that: A dry friction damping structure (36) is provided at the guide mating surface between the floating mounting base (34) and the housing (11).

4. A modular combined high-pressure high-temperature heat pump centrifugal compressor according to claim 1, characterized in that: A thermal compensation washer (37) is provided between the back of the first gear ring (32) and the housing (11). The thermal compensation washer (37) is made of bimetallic or shape memory alloy and is used to generate axial and / or radial deformation when the temperature changes, so as to compensate for the change in meshing clearance between the driven gear (31) and the first gear ring (32) caused by thermal expansion.

5. A modular combined high-pressure high-temperature heat pump centrifugal compressor according to claim 1, characterized in that, Also includes: The stop part (38) is fixed on the housing (11) of the IGV capacity adjustment mechanism device (1) and is used to limit the axial movement range of the floating mounting base (34).

6. A modular combined high-pressure high-temperature heat pump centrifugal compressor according to claim 1, characterized in that: An axial deformation floating gap is provided between the second gear ring (33) and the mounting ring (341). The mounting ring (341) is provided with rollers (391) for supporting the rotation of the second gear ring (33). An elastic element (39) is provided between the mounting ring (341) and the second gear ring (33). The elastic element (39) applies a preload thrust to the second gear ring (33) to move closer to the driven gear (31), so that the second gear ring (33) and the driven gear (31) remain engaged.

7. A modular combined high-pressure high-temperature heat pump centrifugal compressor according to claim 1, characterized in that, Also includes: A limiting ring (4) is located outside all driven gears (31) and connected to the IGV capacity adjustment mechanism (1). Several support covers (44) are provided on the side of the limiting ring (4) facing the driven gear (31). The support covers (44) are slidably connected to the limiting ring (4) along the axial direction of the driven gear (31). An elastic unit three (45) is provided between the limiting ring (4) and the support cover (44). The elastic unit three (45) applies a thrust to the support cover (44) to move closer to the blade (12). A support shaft (312) is coaxially provided on the side of the driven gear (31) away from the blade (12). The end of the support shaft (312) away from the driven gear (31) abuts against the support cover (44) and rotates under the support of the support cover (44).

8. A modular combined high-pressure high-temperature heat pump centrifugal compressor according to claim 1, characterized in that, Also includes: The transmission plate (51) has an arc-shaped opening (113) on its outer side along the circumference. The transmission plate (51) is located inside the arc-shaped opening (113) and slides along the arc-shaped opening (113). The IGV capacity adjustment mechanism (1) is provided with a transmission rod (52) for pushing the transmission plate (51) to move along the arc-shaped opening (113). The transmission rod (52) is connected to an external drive source (53). The transmission plate (51) is located outside the first gear ring (32), and the transmission plate (51) faces the first gear ring (32). A plurality of transmission grooves (511) are provided on one side along the axial direction. A transmission block (321) adapted to the transmission groove (511) is fixedly connected to the outer circle of the first toothed ring (32). The transmission block (321) is located in the transmission groove (511) and fits against the inner wall of the transmission groove (511). When the transmission plate (51) moves along the arc-shaped opening (113), the first toothed ring (32) is driven to rotate circumferentially through the cooperation between the transmission block (321) and the transmission groove (511). The first toothed ring (32) and the transmission block (321) have an movable gap along the axial direction.

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