Rotor transmission structure and screw compressor

Abstract

The invention provides a rotor transmission structure and a screw compressor. The rotor comprises a male rotor arranged in an axial rotation mode and a plurality of female rotors arranged around the male rotor, the transmission structure comprises a driving gear, and the driving gear is installed on the shaft section of the male rotor; each driven gear is mounted on the shaft section of each female rotor, so that the plurality of driven gears are arranged around the driving gear and are meshed with the driving gear; and the inner gear ring is arranged around the driven gears and engaged with the driven gears. When the driven gear is meshed with the inner gear ring and the driving gear at the same time, the rotation stability of the driven gear is remarkably improved. When the rotor rotates reversely, the reverse contact face of the driven gear can be connected with the inner gear ring or the driving gear more quickly, the response speed of the reverse contact face is earlier than that of tooth face contact generated by reverse movement of the rotor body, and therefore the tooth face collision fault caused by sudden change of the movement direction of the rotor is avoided.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a rotor transmission structure and a screw compressor. Background Art

[0002] The screw compressor has two rotors meshing to form tooth grooves, and goes through the action state of open-closed-open, thus completing the process of suction-compression-exhaust. During the meshing process of the screw rotors, there will be mutual friction and collision between the two rotors, so lubricating oil is generally sprayed into the rotor cavity to play a lubricating and cooling effect, protecting the two rotors from damage; the injected lubricating oil is mixed with the compressed gas, discharged together, and may be separated downstream as needed. Regardless of whether oil separation is performed, there will always be a certain amount of lubricating oil in the compressed gas.

[0003] However, in some special application areas, there are some requirements for the compressed gas, including keeping it clean, or the gas itself is prone to chemical reaction with oil and must not come into contact with oil. At this time, oil injection is not allowed in the rotor cavity. In order to ensure that the rotor is not damaged, synchronous gears are used for meshing substitution and torque transmission. Figure 1 As shown, the first control rotor A1 and the second control rotor B1 are essentially consistent with the motion mode of the first control synchronous gear A2 and the second control synchronous gear B2, both of which are meshing rotation, but the meshing clearance of the first control synchronous gear A2 and the second control synchronous gear B2 during unidirectional rotation is smaller than the meshing clearance between the first control rotor A1 and the second control rotor B1, so that before the tooth surfaces of the first control rotor A1 and the second control rotor B1 contact, the tooth surfaces of the first control synchronous gear A2 and the second control synchronous gear B2 first contact and transmit force, so that the first control rotor A1 starts to rotate under the drive of the external driving device (at this time, the first control rotor A1 can be called the active rotor, and the corresponding second control rotor B1 can be called the driven rotor), the first The first control synchronous gear A2 at the end of the control rotor shaft rotates synchronously. Before the tooth surfaces of the first control rotor A1 and the second control rotor B1 contact and start meshing, the first control synchronous gear A2 preferentially meshes with the second control synchronous gear B2, and transmits force, or torque, to the second rotor shaft system where the second control synchronous gear B2 is located, driving the second control rotor to rotate synchronously. Since the gear ratio of the first control synchronous gear A2 and the second control synchronous gear B2 is consistent with the gear ratio of the first control rotor A1 and the second control rotor B1, this working process can be maintained. The tooth surfaces of the first control rotor A1 and the second control rotor B1 cannot contact each other at all times, and the speed ratio transmission inversely proportional to the gear ratio is completed, that is, "synchronous rotation". Since the first control rotor A1 and the second control rotor B1 are not in contact, there is no need to inject lubricating oil or other lubricating media into the rotor cavity, ensuring the cleanliness of the rotor cavity.

[0004] During the operation of the compressor, it will inevitably encounter reverse rotation faults, such as when the motor wiring is connected reversely; at this time, there is a large gap on the reverse driving side of the gear, which is usually significantly larger than the reverse meshing gap of the rotor. At this time, the rotor pair will come into contact, resulting in wear or even jamming faults. Summary of the Invention

[0005] In order to solve the above technical problem that there is a large gap on the reverse driving side of the gear in the prior art, which causes wear or jamming of the rotor when the coaxially rotating rotor rotates reversely, the present invention provides a rotor transmission structure and a screw compressor.

[0006] The technical solution adopted by the present invention is as follows:

[0007] The present invention provides a rotor transmission structure, the rotor includes: a male rotor rotatably arranged axially, and a plurality of female rotors arranged around the male rotor and meshing in a non-contact manner. The transmission structure includes:

[0008] A driving gear, which is installed on the shaft section of the male rotor;

[0009] A plurality of driven gears, each driven gear is installed on the shaft section of each female rotor, so that the plurality of driven gears are arranged around the driving gear and mesh with the driving gear;

[0010] An internal gear ring, which is arranged around the plurality of driven gears and meshes with each of the driven gears.

[0011] Furthermore, the contact time of the transmission teeth of the plurality of driven gears with the transmission teeth of the driving gear is inconsistent.

[0012] Furthermore, the tooth number ratio of the male rotor to the female rotor is equal to the tooth number ratio of the driving gear to the driven gear.

[0013] Furthermore, the number of teeth of the male rotor is greater than the number of female rotors.

[0014] Preferably, the number of teeth of the male rotor is 5, and the number of female rotors is 4.

[0015] The present invention also provides an oil-free screw compressor, including the above-mentioned rotor transmission structure.

[0016] The oil-free screw compressor includes: a housing having an exhaust end and a suction end, and a driving component arranged in the housing to drive the shaft section of the male rotor to rotate.

[0017] Furthermore, a seal cover is provided at a position near the exhaust end of the housing, and the seal cover divides the interior of the housing into an exhaust cavity communicating with the exhaust end and a compression cavity communicating with the suction end.

[0018] Further, exhaust ports corresponding to the number and positions of the female rotors one by one are provided on the cover, and the exhaust start times of each exhaust port are evenly staggered within the same exhaust cycle.

[0019] Further, on the side of the cover facing away from the exhaust end, a plurality of bearing mounting positions are provided for mounting rotor bearings corresponding to the male rotor and the female rotor one by one, and a ring gear bearing is provided on the inner wall of the housing corresponding to the position of the internal gear ring.

[0020] Compared with the prior art, the present invention has the following advantages:

[0021] 1. When the driven gear meshes with the internal gear ring and the driving gear simultaneously, its rotational stability is significantly improved. When the rotor rotates in reverse, the reverse contact surface of the driven gear can engage with the internal gear ring or the driving gear more quickly, and its response speed is earlier than the tooth surface contact caused by the reverse movement of the rotor body, thereby avoiding tooth surface rubbing faults caused by sudden changes in the movement direction of the rotor.

[0022] 2. There are differences in the relative phases between each female rotor and the male rotor during the meshing process. This phase difference causes the opening and closing times of the exhaust ports of each female rotor to be staggered from each other, forming an asynchronous exhaust timing sequence, which reduces the noise of the compressor.

[0023] 3. Since the male rotor is subjected to evenly distributed radial forces in multiple directions with equal magnitudes, force cancellation will inevitably occur, greatly reducing the axial force of the male rotor. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly introduce the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0025] Figure 1 is a schematic structural diagram of the prior art;

[0026] Figure 2 is a gear meshing diagram of the prior art;

[0027] Figure 3 is a schematic structural diagram of the transmission structure in the embodiment of the present invention;

[0028] Figure 4 is a side view of the transmission structure in the embodiment of the present invention;

[0029] Figure 5 is a plan view of the rotor end face of the transmission structure in the embodiment of the present invention;

[0030] Figure 6It is a plan view of the gear end face of the transmission structure in the embodiment of the present invention;

[0031] Figure 7 It is a schematic diagram of the force-bearing structure of the rotor of the transmission structure in the embodiment of the present invention;

[0032] Figure 8 It is a three-dimensional structure diagram of the compressor in the embodiment of the present invention;

[0033] Figure 9 It is a cross-sectional view of the compressor in the embodiment of the present invention;

[0034] Figure 10 It is a front view of the compressor in the embodiment of the present invention;

[0035] Figure 11 It is Figure 10 the X-X cross-sectional view showing the rotor contour in

[0036] Figure 12 It is Figure 10 the X-X cross-sectional view showing the exhaust port in

[0037] 1. Male rotor;

[0038] 2. Female rotor;

[0039] 3. Driving gear;

[0040] 4. Driven gear;

[0041] 5. Internal gear ring;

[0042] 6. Housing; 61. Exhaust end; 62. Suction end; 63. Gear ring bearing;

[0043] 7. Driving assembly;

[0044] 8. Cover;

[0045] 81. Exhaust port;

[0046] 9. Rotor bearing. Detailed implementation manners

[0047] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention clearer and more understandable, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0048] The principle and structure of the present invention will be described in detail below with reference to the accompanying drawings and embodiments.

[0049] In the prior art, for example, the patent with application number 202310370412.3 includes a male rotor and a female rotor meshing with each other and a driving gear and a driven gear meshing with each other; the driving gear is installed on the shaft section of the male rotor; the driven gear includes a main driven gear and a secondary driven gear with the same number of teeth and module, which are coaxially and detachably installed on the shaft section of the female rotor, and the secondary driven gear is circumferentially staggered with the main driven gear, and the secondary driven gear and the main driven gear can be relatively rotated around the axis to change the staggered angle between the two; when the driven gear reverses, the meshing clearance between the driven gear and the driving gear is smaller than the meshing clearance between the male rotor and the female rotor.

[0050] like Figure 2 As shown in the figure, during the transmission process, when the driving gear transmits torque to the driven gear, the current transmission teeth have the process of "approaching" - "contacting" - "disengaging", so the process between the teeth of the two gears is a process of "gap" - "zero gap" - "gap". Note that each tooth is independently on the driving side and the non-driving side, M (driving side) and N (non-driving side) on the gear. "Zero gap" means the moment when the teeth of the current driving gear shift or squeeze the teeth of the driven gear. The so-called zero gap is actually the gap at M is zero, but there must be a gap on the non-driving side at this time, otherwise it will be stuck due to the lack of gap during "approaching" and "disengaging".

[0051] When there is a lag in the driven rotor and the gear or the entire rotor group reverses, this can only be ensured by ensuring that the gaps on both the driving and non-driving sides of the gear are smaller than the gaps on the driving and non-driving sides of the rotor, that is, the total gear meshing clearance is smaller than the rotor meshing clearance, so as to ensure that the rotor will not touch at any time.

[0052] The patent with application number 202310370412.3 can solve the problem of reverse contact surface contact caused by rotor reversal, but fine-tuning is required on site during the assembly process, and slippage may occur after running for a period of time, resulting in increased misalignment.

[0053] In this regard, Figure 3 , 4 As shown, the present invention proposes a rotor transmission structure, comprising: a male rotor 1, a plurality of female rotors 2, a driving gear 3, a plurality of driven gears 4 and an inner gear ring 5. Among them:

[0054] The male rotor 1 is a driving rotor arranged for axial rotation. A plurality of female rotors 2 are arranged around the male rotor 1 and kept in a fixed position. At the same time, the female rotors 2 can perform axial rotation. The number of the plurality of female rotors 2 is greater than or equal to 2. The plurality of female rotors 2 surround the male rotor 1 and are in non-contact meshing. The driving gear 3 is installed on the shaft section of the male rotor 1 and is used to drive other rotor components. A plurality of driven gears 4 are respectively installed on the shaft sections of each female rotor 2, and their distribution mode is to surround the driving gear 3 and mesh with the driving gear 3. The internal gear ring 5 is arranged around the outside of all the driven gears 4 and meshes with the outer tooth surfaces of each driven gear 4.

[0055] As Figure 5 , 6 shown, during operation, the male rotor 1 drives the driving gear 3 on its shaft section to rotate through a driving device, and the driving gear 3 sequentially drives a plurality of driven gears 4 distributed in a surrounding manner. At this time, the shaft ends of each female rotor 2 are meshed with the internal tooth surface of the internal gear ring 5 through synchronous gears. The rotation of the internal gear ring 5 further restricts the axial rotation trajectory of the driven gears 4. At the same time, the meshing period of the internal gear ring 5 and the driven gears 4 is different from the meshing period of the driven gears 4 and the driving gear 3. The small gap constraints brought by the meshing of the internal gear ring 5 with a plurality of driven gears 4 respectively make the plurality of driven gears 4 have good rotational stability after meshing with the internal gear ring 5 and the driving gear 3 respectively.

[0056] This design significantly improves the rotational stability of the driven gears 4 when they are meshed with the internal gear ring 5 and the driving gear 3 at the same time. When the rotor rotates in reverse, the reverse contact surface of the driven gear 4 can be engaged with the internal gear ring 5 or the driving gear 3 more quickly, and its response speed is earlier than the tooth surface contact generated by the reverse movement of the rotor body, thus avoiding the tooth surface rubbing fault caused by the sudden change of the rotor movement direction.

[0057] As Figure 7 shown, since the male rotor is subjected to uniformly distributed radial forces in multiple directions with equal magnitudes, such as 4-direction radial forces in this implementation scheme, this will inevitably result in the cancellation of forces, greatly reducing the axial force of the male rotor.

[0058] Specifically, the meshing periods of the plurality of driven gears 4 and the driving gear 3 are designed to be staggered, so that the contact times of some of the driven gears 4 and the driving gear 3 do not coincide; that is, the contact times of the driving teeth of some or all of the driven gears 4 and the driving teeth of the driving gear 3 are inconsistent. Because there will be certain tolerances in the production and installation of the driven gears 4, in actual situations, there will be slight differences in the contact meshing times of each driven gear 4 and the driving gear 3.

[0059] The complete process of the driving gear 3 from approaching meshing (i.e., the driving side of the teeth of the driving gear and the driven side of the driven gear are in the state of maximum clearance) to contact meshing (i.e., the driving side of the teeth of the driving gear is in contact with the driven side of the driven gear) is defined as one meshing cycle. Before the driving gear 3 reverses, if one of the driven gears 4 is in the state of contact meshing with the driving gear 3, then there will be other driven gears 4 in the state of approaching meshing with the driving gear 3. When reversing occurs, the clearance between the driven side of the driven gear 4 in the contact meshing state and the driving side of the driving gear 3 is the largest at this time, while the clearance between the driven side of the driven gear 4 in the approaching meshing state and the driving side of the driving gear 3 is small. This driven gear 4 then drives the internal gear ring 5 (since the internal gear ring 5 has internal teeth and the meshing form with the external teeth of the driven and driving gears 3 is different, and its meshing clearance is smaller), causing other driven gears 4 to rotate accordingly, thereby achieving the effect of avoiding jamming and avoiding rotor contact at the same time.

[0060] In a specific embodiment, the tooth number ratio of the male rotor 1 to the female rotor 2 is equal to the tooth number ratio of the driving gear 3 to the driven gear 4. The number of teeth of the male rotor 1 is Z1, the number of teeth of the female rotor 2 is Z2, the number of teeth of the driving gear 3 is GZ1, the number of teeth of each driven gear 4 is GZ2, and the number of teeth of the internal gear ring 5 is GZ3. The number of teeth of the male rotor 1 Z1 / the number of teeth of the female rotor 2 Z2 = the number of teeth of the driving gear 3 GZ1 / the number of teeth of the driven gear 4 GZ2. When the rotational speed of the male rotor 1 is α, the rotational speed of the driving gear 3 is α, the rotational speeds of the female rotor 2 and the driven gear 4 are α·Z1 / Z2, or α·GZ1 / GZ2, and the rotational speed of the internal gear ring 5 is α·GZ1 / GZ3.

[0061] By setting the tooth number ratios to be the same, the meshing interference phenomenon caused by the difference in the transmission speed ratios between the rotors and the gears can be avoided during the operation of the transmission structure. When the male rotor 1 is driven to rotate by an external driving device, the meshing transmission between the driving gear 3 and the driven gear 4 can transmit the relative motion relationship between the rotors. At the same time, the meshing between the internal gear ring 5 and the driven gear 4 further restricts the motion trajectory of the gear system. This design enables the transmission structure to maintain a stable power transmission path during the forward and reverse rotation switching, reducing the gear meshing impact and improving the transmission accuracy.

[0062] In a specific embodiment, in the rotor transmission structure, the number of teeth of the male rotor 1 is designed to be more than that of the female rotor 2, so that the exhaust ports 81 corresponding to each female rotor 2 form an asynchronous exhaust cycle. When the male rotor 1 rotates, its tooth surface meshes with the circumferentially distributed female rotors 2 in sequence. Since the number of teeth of the male rotor 1 is more than the total number of teeth of the female rotors 2, there is a difference in the relative phase between each female rotor 2 and the male rotor 1 during the meshing process. This phase difference causes the opening and closing times of the exhaust ports of each female rotor 2 to be staggered from each other, forming a non-synchronized exhaust timing sequence.

[0063] Through the above structural design, the exhaust process of each female rotor 2 exhibits a time distribution characteristic. When a certain female rotor 2 is in the state of fully open exhaust port, the adjacent female rotor 2 may be in the stage of closed or partially open exhaust port. This asynchronous exhaust mode effectively disperses the concentrated pressure fluctuations in the traditional synchronous exhaust structure and reduces the amplitude of exhaust pulsation. At the same time, the staggered exhaust cycles extend the effective flow time of a single exhaust port and reduce the fluid excitation phenomenon caused by the instantaneous flow rate mutation.

[0064] In a preferred embodiment, as Figure 5 , 6 shown, the number of teeth of the male rotor 1 is set to 5, and the number of female rotors 2 distributed around it is 4. This configuration makes the number of teeth of the male rotor 1 and the number of female rotors 2 form a non-integer multiple relationship. Specifically, when the male rotor 1 rotates one week, the meshing phases of its tooth surface with each female rotor 2 are staggered in turn. This high-density timing distribution significantly increases the frequency of exhaust pulsation and at the same time reduces the flow rate amplitude fluctuation of a single exhaust. This design further enhances the dynamic stability of the transmission system. At the same time, under such a scheme, the exhaust volume brought by multiple female rotors 2 is higher than that of a single male rotor 1 and female rotor 2 of the same size (taking 4 female rotors 2 as an example, the displacement is 4 times that of a single rotor pair), but the overall size does not increase, especially the outer dimensions of the length, width and height of the whole machine do not change.

[0065] As Figures 8 to 10 shown, the present invention also proposes a screw compressor, which can specifically be an oil-free (no lubricating oil in the rotor area) screw compressor, including a housing 6 with a compression cavity, a rotor transmission structure, and a drive assembly 7 for driving the rotor transmission structure. The rotor transmission structure adopts the aforementioned transmission structure, specifically including a male rotor 1, a female rotor 2, a driving gear 3, a driven gear 4, and an internal gear ring 5. The male rotor 1 is axially arranged at the center of the compression cavity, and multiple female rotors 2 are distributed around the male rotor 1. The driving gear 3 is installed on the shaft section of the male rotor 1, multiple driven gears 4 are respectively arranged on the shaft sections of the respective female rotors 2, and the internal gear ring 5 is arranged outside the driven gear 4 and meshes with it.

[0066] During operation, the drive assembly 7 drives the male rotor 1 to rotate, and the driving gear 3 drives the driven gears 4 to make the female rotors 2 rotate synchronously. The tooth surfaces of the male rotor 1 and the female rotor 2 form a dynamic sealing volume in the compression cavity, and continuous cycles of suction, compression, and exhaust are achieved through the speed ratio matching of the gear transmission structure. The secondary meshing constraint between the internal gear ring 5 and the driven gear 4 ensures the rotational stability of the transmission system under high pressure difference conditions.

[0067] The meshing clearance of the rotor tooth surface is precisely controlled by the bilateral meshing clearance of the gear transmission system, eliminating the dependence on the traditional oil lubrication sealing structure. When reverse rotation occurs, the preferential contact characteristic between the driven gear 4 and the internal gear ring 5 can quickly establish a reverse torque transmission path to prevent damage to the rotor tooth surface due to rubbing.

[0068] In a specific embodiment, the oil-free screw compressor includes a housing 6 and a drive assembly 7 (which can also be an external drive assembly, both within the protection scope of the present invention). The outer peripheral surface of the housing 6 is circular, with an exhaust end 61 and a suction end 62 at both ends respectively. The drive assembly 7 is installed inside the housing 6 and directly acts on the shaft section of the male rotor 1 to drive the male rotor 1 to rotate. The exhaust end 61 and the suction end 62 of the housing 6 are respectively connected to an external pipeline system for sucking and compressing and transporting gas.

[0069] When the drive assembly 7 starts, it drives the rotation of the shaft section of the male rotor 1. The driving gear 3 of the male rotor 1 then drives the surrounding driven gears 4, causing the female rotor 2 to rotate synchronously. The tooth surfaces of the male rotor 1 and the female rotor 2 form a dynamic sealing volume in the compression cavity. Gas is inhaled through the suction end 62 and gradually compressed, and then output through the exhaust end 61. The secondary meshing constraint between the internal gear ring 5 and the driven gear 4 ensures the rotational stability of the transmission system under high pressure difference conditions, avoiding meshing failure caused by load fluctuations.

[0070] This design optimizes the overall structure through the integrated layout of the drive assembly 7 and the housing 6. The compact installation method of the drive assembly 7 reduces the space occupied by traditional external drive devices, shortens the power transmission path at the same time, and reduces mechanical losses. The exhaust end 61 and the suction end 62 of the housing 6 adopt a symmetric distribution design, making the gas flow path more balanced and reducing local flow resistance losses.

[0071] In a specific embodiment, the cover 8 is fixedly installed at a position of the housing 6 close to the exhaust end 61. Its main body can adopt an annular structure nested on the inner wall of the housing 6 and form a sealed connection with the housing 6 by means of bolts or welding. An exhaust port 81 is opened in the area of the cover 8 close to the center.

[0072] The partitioning function of the cover 8 divides the inside of the housing 6 into two independent areas: a compression cavity and an exhaust cavity. The compression cavity is located on the side of the cover 8 facing the suction end 62 and houses the drive assembly 7 and the rotor transmission structure; the exhaust cavity is located on the side of the cover 8 facing the exhaust end 61 and is communicated with the compression cavity through the exhaust port 81 of the cover 8. When the male rotor 1 is driven to rotate by the drive assembly 7, the rotor transmission structure drives the female rotor 2 to rotate synchronously. The tooth surfaces of the male rotor 1 and the female rotor 2 form a dynamic sealing volume in the compression cavity, completing the process of gas inhalation and compression. The compressed high-pressure gas enters the exhaust cavity through the exhaust port 81 of the cover 8 and is output to the external pipeline system through the exhaust end 61 of the housing 6. The overall structure is simple and reliable, and the assembly is convenient.

[0073] Such as Figure 11 、 12As shown, the exhaust port 81 serves as the gas flow passage between the compression chamber and the exhaust chamber. Its cross-sectional shape and size are designed according to the compressed gas flow rate requirements, and can be in the form of circular, elliptical or polygonal hole arrays. The exhaust port 81 is provided on the cover 8, specifically located in the tooth groove area facing each female rotor. Its quantity and position correspond to the exhaust cycle characteristics of the rotor drive structure (such as the non-integer multiple ratio of the 5-tooth male rotor 1 and the 4 female rotors 2). By the directional setting of the exhaust port 81, the gas flow path is optimized, enabling the asynchronous exhaust process of each female rotor 2 to achieve flow superposition through the exhaust port 81. This distribution design reduces the local eddy current loss caused by the traditional centralized exhaust port 81. The staggered exhaust cycles extend the effective flow time of a single exhaust port, reducing the fluid excitation phenomenon caused by the instantaneous flow rate mutation.

[0074] In addition, the edge of the exhaust port 81 is processed with chamfers or streamlined transitions to further improve the air flow through efficiency.

[0075] Specifically, on the side of the cover 8 facing away from the exhaust end 61, a plurality of bearing mounting positions are distributed circumferentially. Their quantity matches the total number of shaft ends of the male rotor 1 and the female rotors 2 (for example, 1 male rotor 1 and 4 female rotors 2 correspond to 5 bearing mounting positions). Each bearing mounting position is equipped with a rotor bearing 9, respectively corresponding to support the shaft ends of the male rotor 1 and the female rotors 2, ensuring the rotational stability of the rotors in the compression chamber. The bearings can compensate for assembly errors through gaskets or hydraulic locking devices to maintain the uniformity of the meshing clearance between the rotor tooth surfaces.

[0076] On the inner wall of the housing 6, a ring gear bearing 63 is provided at the radial position corresponding to the internal gear ring 5. This bearing is an annular rolling bearing arranged around the outer edge of the internal gear ring 5. The support surface of the ring gear bearing 63 is coaxial with the rotation axis of the internal gear ring 5, and its load-bearing direction includes both radial and axial components, ensuring that the internal gear ring 5 maintains the meshing accuracy with the driven gear 4 when transmitting torque.

[0077] The axial displacements of the shaft ends of the male rotor 1 and the female rotors 2 are directly restricted by the rotor bearings 9; the ring gear bearing 63 indirectly stabilizes the meshing state of the driven gear 4 by restricting the movement trajectory of the internal gear ring 5. When the drive system bears load fluctuations, the elastic deformation of the bearings can absorb part of the vibration energy, avoiding stress concentration in the gear meshing area.

[0078] In addition, the gear part can be placed in a dedicated gearbox structure, which is convenient for the gear to be lubricated with special lubricating oil separately, preventing the lubricating oil from entering the air passage of the compressor.

[0079] Specifically, one end of the shaft of the male rotor 1 is limited by the rotor bearing 9, and the other end extends towards the suction end 62. The drive assembly 7 is installed in the compressor cavity and specifically includes: a stator that surrounds the shaft section at the other end of the male rotor 1 and is fixed to the housing, and a rotor that is arranged on the shaft section at the other end of the male rotor 1. That is, the drive assembly 7 is a drive motor that can drive the male rotor 1 to rotate and provide driving force.

[0080] In addition, the drive assembly can also be external, not limited to the above form, as long as it can provide the driving force for the rotation of the male rotor.

[0081] It should be noted that the terms used above are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present invention. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0082] Unless otherwise specifically stated, the relative arrangements, numerical expressions, and numerical values of the components and steps set forth in these embodiments do not limit the scope of the present invention. At the same time, it should be understood that for the convenience of description, the dimensions of the various parts shown in the drawings are not drawn in actual proportional relationships. Technologies, methods, and devices known to those of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the said technologies, methods, and devices should be regarded as part of the authorized specification. In all the examples shown and discussed here, any specific value should be construed as merely exemplary and not as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that like reference numerals and letters denote like items in the following drawings, and thus, once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0083] In the description of the present invention, it should be understood that the orientation or positional relationships indicated by orientation words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal", and "top, bottom" are generally based on the orientation or positional relationships shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description. Without contrary explanation, these orientation words do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting the protection scope of the present invention; the orientation words "inside, outside" refer to the inside and outside relative to the outline of each component itself.

[0084] For ease of description, spatial relative terms such as "above", "over", "on the upper surface", "upper" etc. can be used here to describe the spatial positional relationship of a device or feature shown in the figures with other devices or features. It should be understood that the spatial relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is inverted, a device described as "above" or "over" other devices or structures will then be positioned "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both the orientations of "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and corresponding interpretations should be made for the spatial relative descriptions used here.

[0085] In addition, it should be noted that using words such as "first", "second" etc. to define components is only for the convenience of differentiating the corresponding components. Without additional statements, the above words have no special meanings, and thus cannot be construed as limiting the protection scope of the present invention.

[0086] The above are only the preferred embodiments of the present invention and are not used to limit the present invention. For those skilled in the art, the present invention can have various modifications and variations. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A rotor drive structure, characterized in that, The rotor includes: A male rotor arranged to rotate axially, and a plurality of female rotors arranged around the male rotor and meshing non - contactingly. The transmission structure includes: A driving gear, which is mounted on the shaft section of the male rotor; A plurality of driven gears, each driven gear is mounted on the shaft section of each female rotor, so that the plurality of driven gears are arranged around the driving gear and mesh with the driving gear; An internal gear ring, which is arranged around the plurality of driven gears and meshes with each of the driven gears.

2. The rotor drive structure according to claim 1, characterized in that, The contact times of the driving teeth of the plurality of driven gears and the driving teeth of the driving gear are inconsistent.

3. The rotor drive structure according to claim 1, characterized in that, The tooth number ratio of the male rotor to the female rotor is equal to the tooth number ratio of the driving gear to the driven gear.

4. The rotor drive structure according to any one of claims 1 to 3, characterized in that, The number of teeth of the male rotor is greater than the number of female rotors.

5. The rotor drive structure according to any one of claims 1 to 3, characterized in that, The number of teeth of the male rotor is 5, and the number of female rotors is 4.

6. A screw compressor, comprising: It is characterized in that It includes the rotor transmission structure according to any one of claims 1 to 5.

7. The screw compressor according to claim 6, wherein, The screw compressor includes: a housing having an exhaust end and a suction end, and a driving assembly arranged inside or outside the housing to drive the shaft section of the male rotor to rotate.

8. The screw compressor according to claim 7, wherein, A cover is provided at a position near the exhaust end inside the housing, and the cover divides the inside of the housing into an exhaust cavity communicating with the exhaust end and a compression cavity communicating with the suction end.

9. The screw compressor according to claim 8, wherein, The cover is provided with exhaust ports corresponding one - to - one to the number and positions of the female rotors, and the exhaust start times of each exhaust port are evenly staggered within the same exhaust cycle.

10. The screw compressor according to claim 8, wherein A plurality of bearing mounting positions are provided on the side of the cover facing away from the exhaust end for mounting rotor bearings corresponding one - to - one to the male rotor and the female rotor, and a gear ring bearing is provided on the inner wall of the housing corresponding to the setting position of the internal gear ring.

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