High-pressure compressor shaft seal seat pressure-bearing structure

Abstract

This utility model discloses an optimized pressure-bearing structure for a high-pressure compressor shaft seal seat, including a male rotor and an exhaust end seat of the compressor. The exhaust end seat houses a roller bearing, a four-point bearing, and a high-pressure shaft seal seat. A shaft seal assembly is mounted on the male rotor, forming a flushing fluid cavity between the shaft seal assembly and the high-pressure shaft seal seat. The key design features include a shaft seal seat sleeve with a pressure-bearing ring at its outer end. This ring abuts against one end face of a disc spring, while the other end face of the disc spring abuts against a high-pressure cover. The inner diameter of the pressure-bearing ring is larger than the inner diameter of the disc spring, allowing the space occupied by the disc spring to communicate with the flushing fluid cavity. This design, without altering the exhaust end seat structure, counteracts the unidirectional pressure of the flushing fluid on the high-pressure shaft seal seat, preventing the flushing fluid from exerting external pressure on the high-pressure shaft seal seat. This, in turn, increases the clamping force on the outer ring of the four-point bearing of the high-pressure compressor, extends the service life of the high-pressure compressor, and ensures safe and stable operation of the high-pressure compressor.

Description

Technical Field

[0001] This utility model relates to high-pressure compressors, specifically a pressure-bearing structure for a high-pressure compressor shaft seal seat. Background Technology

[0002] In the field of compressor technology, compressors can be classified into conventional compressors and high-pressure compressors according to their design pressure. Conventional compressors have a design pressure P ≤ 2.5 MPa, while high-pressure compressors have a design pressure of 2.5 MPa < P ≤ 4.0 MPa. In existing technology, the compressor rotor is supported on roller bearings and four-point bearings arranged adjacent to each other within the exhaust end seat. The roller bearings bear the radial load generated by the exhaust pressure, while the four-point bearings bear the axial thrust generated by the exhaust pressure. The higher the exhaust pressure, the greater the thrust exerted by the rotor on the four-point bearings, and the greater the clamping force required for the four-point bearings. With the increasingly widespread application of high-pressure compressors, how to improve the clamping force of the outer ring of the four-point bearings in high-pressure compressors, thereby ensuring the safety performance of the high-pressure compressor and effectively extending its service life, has always been an important research topic for those skilled in the art. Summary of the Invention

[0003] The purpose of this utility model is to provide a pressure-bearing structure for a high-pressure compressor shaft seal seat, which can effectively increase the clamping force of the outer ring of the four-point bearing of the high-pressure compressor while keeping the basic structure of the exhaust end seat unchanged, thereby extending the working life of the high-pressure compressor and ensuring the safe and stable operation of the high-pressure compressor.

[0004] To achieve the above objectives, the high-pressure compressor shaft seal bearing structure designed in this utility model includes a male rotor of the compressor and an exhaust end seat. A roller bearing, an adjusting ring, a four-point bearing, and a high-pressure shaft seal seat are sequentially arranged in the inner cavity of the exhaust end seat. The journal bearing section of the male rotor is nested in the bearing holes of the roller bearing, adjusting ring, and four-point bearing. This combined bearing is used to bear the radial load and axial thrust generated by the exhaust pressure of the male rotor. A locking nut is provided on the threaded section of the journal of the male rotor to fix the inner ring of the four-point bearing. The journal sealing section of the male rotor is provided with a shaft seal assembly that mates with the high-pressure shaft seal seat to ensure the sealing performance of the male rotor. A flushing fluid cavity is formed between the shaft seal assembly and the high-pressure shaft seal seat. Flushing fluid channels connected to the flushing fluid cavity are provided on the exhaust end seat and the high-pressure shaft seal seat to complete the water sealing and water flushing of the shaft seal assembly in real time during operation. The high-pressure shaft seal seat has a disc spring and a high-pressure cover on its outer side. The high-pressure cover is fixed to the exhaust end seat by screws arranged circumferentially to abut and press against the high-pressure shaft seal seat. Its special feature is that the high-pressure shaft seal seat has a shaft seal seat sleeve. The inner end of the shaft seal seat sleeve abuts against the outer ring of the four-point bearing. The outer end of the shaft seal seat sleeve is provided with a pressure-bearing ring platform. The pressure-bearing ring platform abuts against one end face of the disc spring, and the other end face of the disc spring abuts against the high-pressure cover. The inner diameter of the pressure-bearing ring platform is larger than the inner diameter of the disc spring, thus connecting the space occupied by the disc spring with the flushing fluid cavity. In this way, without changing the structure of the exhaust end seat cavity, by optimizing the design of the high-pressure shaft seal seat structure, the flushing fluid entering the flushing fluid cavity can simultaneously fill both sides of the pressure-bearing ring platform, thereby offsetting the unidirectional pressure of the flushing fluid on the high-pressure shaft seal seat and preventing the flushing fluid from creating external pressure on the high-pressure shaft seal seat, thus improving the clamping force on the four-point bearing.

[0005] As a preferred embodiment, the shaft seal sleeve is recessed and installed within the inner cavity of the exhaust end seat, thereby creating an axial length difference between the pressure-bearing ring and the outer end of the exhaust end seat. The high-pressure gland has a gland disc and a gland boss. The gland disc is fixed to the exhaust end seat by screws arranged circumferentially, and the gland boss extends into the inner cavity of the exhaust end seat through the length difference, abutting against the other end face of the disc spring. Compared with the conventional compressor shaft seal bearing structure, the high-pressure shaft seal sleeve is designed to be shorter, and the high-pressure gland design adds a gland boss. After the gland boss extends into the inner cavity of the exhaust end seat, the shorter shaft seal sleeve is pressed by the disc spring. This provides a stable clamping force for the high-pressure shaft seal and enhances the sealing performance of the high-pressure gland. More importantly, this structural change ensures that the space occupied by the disc spring is stably integrated and connected with the flushing fluid cavity, and the disc spring is always immersed in the flushing fluid. This more effectively counteracts the unidirectional pressure of the flushing fluid on the outer bearing ring of the shaft seal sleeve, resulting in a greater clamping force ultimately transmitted to the outer ring of the four-point bearing.

[0006] Furthermore, at least one sealing ring mounting groove is provided on the outer wall of the gland boss. In this way, by adding a sealing ring to the outer wall of the gland boss, the improved high-pressure gland can be guaranteed to have a stable and reliable seal.

[0007] Furthermore, the pressure plate disc is provided with an oil drain channel. This allows excess lubricating oil inside the high-pressure pressure plate to be drained in real time, ensuring stable operation of the compressor.

[0008] Furthermore, the final section of the flushing fluid channel is located on the pressure-bearing ring. This balanced channel structure allows the flushing fluid entering the flushing fluid cavity to exert more even pressure on both ends of the pressure-bearing ring, thus more stably and reliably counteracting the unidirectional pressure of the flushing fluid on the pressure-bearing ring.

[0009] The advantages of this invention are as follows: By improving the structure and shape of the high-pressure shaft seal seat and the high-pressure gland, the flushing fluid entering the flushing fluid cavity can act simultaneously on both sides of the pressure-bearing ring of the high-pressure shaft seal seat, offsetting the unidirectional pressure of the flushing fluid on the high-pressure shaft seal seat. This prevents the flushing fluid from creating external pressure on the high-pressure shaft seal seat, thereby resulting in a greater clamping force ultimately transmitted to the outer ring of the four-point bearing. This invention can effectively increase the clamping force of the outer ring of the four-point bearing without changing the structure of the exhaust end seat, improving the safety performance of the high-pressure compressor, ensuring stable operation of the high-pressure compressor, and extending the service life of the high-pressure compressor. It is suitable for widespread application in various types of high-pressure compressors. Attached Figure Description

[0010] Figure 1 This is a cross-sectional schematic diagram of a conventional compressor shaft seal bearing structure.

[0011] Figure 2 This is a cross-sectional schematic diagram of a pressure-bearing structure for a high-pressure compressor shaft seal seat.

[0012] Figure 3 for Figure 2 Enlarged cross-sectional view of the medium and high pressure shaft seal seat.

[0013] Figure 4 for Figure 2 Enlarged cross-sectional view of the medium and high pressure gland.

[0014] The components in the diagram are labeled as follows: 1. Roller bearing; 2. Adjusting ring; 3. Four-point bearing; 4. Exhaust end seat; 5. Locking nut; 6. Shaft seal assembly; 7. Flushing fluid cavity; 8. High-pressure shaft seal seat (including: shaft seal seat sleeve 8a, pressure ring platform 8b); 9. Flushing fluid channel; 10. Disc spring; 11. High-pressure gland (including: gland disc 11a, gland boss 11b, sealing ring mounting groove 11c, oil drain channel 11d); 12. Screw; 13. Male rotor; 14. Conventional shaft seal seat; 15. Conventional gland. Detailed Implementation

[0015] The present invention will be further described in detail below with reference to the accompanying drawings, comparative examples and embodiments, but these embodiments should not be construed as limiting the present invention.

[0016] Comparative example: like Figure 1 The diagram shows a conventional compressor shaft seal bearing structure in the prior art, comprising a male rotor 13 and an exhaust end seat 4. A roller bearing 1, an adjusting ring 2, a four-point bearing 3, and a conventional shaft seal seat 14 are sequentially arranged within the inner cavity of the exhaust end seat 4. The journal bearing section of the male rotor 13 is nested in the bearing holes of the roller bearing 1, the adjusting ring 2, and the four-point bearing 3. A locking nut 5 is provided on the threaded section of the journal of the male rotor 13, and a shaft seal assembly 6 is provided on the sealing section of the journal of the male rotor 13 to mate with the conventional shaft seal seat 14. A flushing fluid cavity 7 is formed between the shaft seal assembly 6 and the conventional shaft seal seat 14. Flushing fluid channels 9 connected to the flushing fluid cavity 7 are provided on the exhaust end seat 4 and the conventional shaft seal seat 14. A disc spring 10 and a conventional pressure cap 15 are provided on the outer side of the conventional shaft seal seat 14. The conventional pressure cap 15 is fixed to the exhaust end seat 4 by screws 12 arranged circumferentially.

[0017] from Figure 1 As shown in the conventional compressor shaft seal bearing structure, the outer end of the conventional shaft seal 14 is flush with the outer end face of the exhaust end seat 4. The conventional pressure cap 15 is entirely located on the outer end face of the exhaust end seat 4, and the disc spring 10 is entirely mounted outside the exhaust end seat 4. The conventional shaft seal 14 separates the flushing fluid cavity 7 from the space occupied by the disc spring 10, preventing the flushing fluid from entering the space occupied by the disc spring 10. The pressure exerted by the disc spring 10 on the conventional shaft seal 14 is F1, and the counter-pressure exerted by the flushing fluid in the flushing fluid cavity 7 on the conventional shaft seal 14 is F2. Therefore, the clamping force transmitted by the conventional shaft seal 14 to the outer ring of the four-point bearing 3 is F1-F2.

[0018] Example: like Figures 2-4The diagram illustrates a pressure-bearing structure for a high-pressure compressor shaft seal seat, comprising a male rotor 13 and an exhaust end seat 4. A roller bearing 1, an adjusting ring 2, a four-point bearing 3, and a high-pressure shaft seal seat 8 are sequentially arranged within the inner cavity of the exhaust end seat 4. The journal bearing section of the male rotor 13 is nested within the bearing holes of the roller bearing 1, the adjusting ring 2, and the four-point bearing 3, with the roller bearing 1 and the four-point bearing 3 respectively bearing the radial load and axial thrust generated by the exhaust pressure of the male rotor 13. A locking nut 5 is provided on the threaded section of the journal of the male rotor 13 to secure the inner ring of the four-point bearing 3. A shaft seal assembly 6, which mates with the high-pressure shaft seal seat 8, is provided on the sealing section of the journal of the male rotor 13 to ensure the sealing performance of the male rotor 13. A flushing fluid cavity 7 is formed between the shaft seal assembly 6 and the high-pressure shaft seal seat 8. Flushing fluid channels 9, connected to the flushing fluid cavity 7, are provided on the exhaust end seat 4 and the high-pressure shaft seal seat 8 to perform real-time water sealing and flushing of the shaft seal assembly 6 during operation. A disc spring 10 and a high-pressure cover 11 are provided on the outside of the high-pressure shaft seal seat 8. The high-pressure cover 11 is fixed to the exhaust end seat 4 by screws 12 arranged in the circumferential direction, and is used to press the high-pressure shaft seal seat 8.

[0019] The aforementioned high-pressure shaft seal seat 8 has a shaft seal seat sleeve 8a. The inner end of the shaft seal seat sleeve 8a abuts against the outer ring of the four-point bearing 3. The outer end of the shaft seal seat sleeve 8a is provided with a pressure bearing ring platform 8b, which abuts against one end face of the disc spring 10. The other end face of the disc spring 10 abuts against the high-pressure cover 11. The inner diameter of the pressure bearing ring platform 8b is designed to be larger than the inner diameter of the disc spring 10, so that the space occupied by the disc spring 10 can be connected to the flushing fluid cavity 7.

[0020] Specifically, the shaft seal sleeve 8a is recessed and installed in the inner cavity of the exhaust end seat 4, thereby creating an axial length difference between the pressure bearing ring 8b and the outer end of the exhaust end seat 4. The high-pressure cover 11 has a cover disc 11a and a cover boss 11b. The cover disc 11a is fixed to the exhaust end seat 4 by screws 12 arranged circumferentially. The cover boss 11b extends into the inner cavity of the exhaust end seat 4 through the aforementioned length difference and abuts against the other end face of the disc spring 10.

[0021] In this embodiment, a sealing ring mounting groove 11c is provided on the outer wall of the gland boss 11b. By adding an outer wall sealing ring, the sealing performance of the high-pressure gland 11 can be ensured to be more stable and reliable. An oil drain channel 11d is provided on the gland disc 11a to promptly drain excess lubricating oil from the high-pressure gland 11 during the operation of the high-pressure compressor, ensuring stable operation of the compressor.

[0022] In this embodiment, the final section of the flushing fluid channel 9 is located on the pressure-bearing ring platform 8b. This balanced arrangement of the channel structure allows the flushing fluid entering the flushing fluid cavity 7 to exert more even pressure on both ends of the pressure-bearing ring platform 8b, thus more stably and reliably counteracting the unidirectional pressure of the flushing fluid on the pressure-bearing ring platform 8b.

[0023] from Figures 2-4 As shown in the pressure-bearing structure of the high-pressure compressor shaft seal seat, the outer end of the shaft seal sleeve 8a of the high-pressure shaft seal seat 8 is recessed into the outer end face of the exhaust end seat 4. The pressure cover boss 11b of the high-pressure cover 11 extends into the inner cavity of the exhaust end seat 4, and the disc spring 10 is integrally installed inside the exhaust end seat 4. The inner diameter of the pressure-bearing ring 8b of the high-pressure shaft seal seat 8 is larger than the inner diameter of the disc spring 10, forming a central annular channel, which connects the space occupied by the disc spring 10 with the flushing fluid cavity 7, allowing the flushing fluid to enter the space occupied by the disc spring 10 in real time. The pressure F1 generated by the disc spring 10 on the high-pressure shaft seal seat 8 is the flushing fluid. The flushing fluid in the flushing fluid cavity 7 acts on both sides of the pressure-bearing ring 8b simultaneously, with the pressure on both sides being the same but in opposite directions. The pressure F2 generated by the flushing fluid on the high-pressure shaft seal seat 8 is zero. Therefore, the clamping force transmitted by the high-pressure shaft seal seat 8 to the outer ring of the four-point bearing 3 is F1.

[0024] and Figure 1 Compared to the conventional shaft seal bearing structure shown, this invention, by changing the structural form of the high-pressure shaft seal 8 and the high-pressure cover 11, counteracts the pressure of the flushing fluid on the high-pressure shaft seal 8, resulting in a greater clamping force ultimately transmitted to the outer ring of the four-point bearing 3. For the high-pressure compressor, its structure is more rational, more conducive to the clamping and fixing of the four-point bearing 3, thereby improving the safety performance of the high-pressure compressor.

[0025] In summary, by means of the technical solution of this utility model, the clamping force of the high-pressure shaft seal on the outer ring of the four-point bearing can be significantly increased without changing the structure of the exhaust end seat, ensuring the safety performance of the high-pressure compressor, ensuring the stable operation of the high-pressure compressor, and thus effectively extending the working life of the high-pressure compressor. It is suitable for promotion and application in various types of high-pressure compressors.

[0026] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. A pressure-bearing structure for a high-pressure compressor shaft seal seat, comprising a male rotor (13) and an exhaust end seat (4) of the compressor, wherein a roller bearing (1), an adjusting ring (2), a four-point bearing (3) and a high-pressure shaft seal seat (8) are sequentially arranged in the inner cavity of the exhaust end seat (4); the journal bearing section of the male rotor (13) is nested in the bearing holes of the roller bearing (1), the adjusting ring (2) and the four-point bearing (3), and a locking nut (5) is provided on the threaded section of the journal of the male rotor (13); the journal of the male rotor (13) is sealed with a high-pressure shaft seal seat (8). The sealing section is provided with a shaft seal assembly (6) that cooperates with the high-pressure shaft seal seat (8); a flushing fluid cavity (7) is formed between the shaft seal assembly (6) and the high-pressure shaft seal seat (8), and flushing fluid channels (9) connected to the flushing fluid cavity (7) are provided on the exhaust end seat (4) and the high-pressure shaft seal seat (8); a disc spring (10) and a high-pressure cover (11) are provided on the outside of the high-pressure shaft seal seat (8), and the high-pressure cover (11) is fixed to the exhaust end seat (4) by screws (12) arranged circumferentially; characterized in that: The high-pressure shaft seal seat (8) has a shaft seal seat sleeve (8a). The inner end of the shaft seal seat sleeve (8a) abuts against the outer ring of the four-point bearing (3). The outer end of the shaft seal seat sleeve (8a) is provided with a pressure bearing ring platform (8b). The pressure bearing ring platform (8b) abuts against one side of the disc spring (10). The other side of the disc spring (10) abuts against the high-pressure cover (11). The inner diameter of the pressure bearing ring platform (8b) is larger than the inner diameter of the disc spring (10), so that the space occupied by the disc spring (10) is connected to the flushing fluid cavity (7).

2. The high-pressure compressor shaft seal bearing structure according to claim 1, characterized in that: The shaft seal sleeve (8a) is recessed and installed in the inner cavity of the exhaust end seat (4), thereby forming an axial length difference between the pressure bearing ring (8b) and the outer end of the exhaust end seat (4); the high pressure cover (11) has a cover disc (11a) and a cover boss (11b). The cover disc (11a) is fixed to the exhaust end seat (4) by screws (12) arranged circumferentially. The cover boss (11b) extends into the inner cavity of the exhaust end seat (4) through the length difference and abuts against the other end face of the disc spring (10).

3. The high-pressure compressor shaft seal bearing structure according to claim 2, characterized in that: At least one sealing ring mounting groove (11c) is provided on the outer wall of the gland boss (11b).

4. The high-pressure compressor shaft seal bearing structure according to claim 2 or 3, characterized in that: An oil drain channel (11d) is provided on the capping disc (11a).

5. The high-pressure compressor shaft seal bearing structure according to claim 1, 2, or 3, characterized in that: The final section of the flushing fluid channel (9) is located on the pressure ring platform (8b), thereby making the flushing fluid entering the flushing fluid cavity (7) apply more even pressure to both ends of the pressure ring platform (8b).

6. The high-pressure compressor shaft seal bearing structure according to claim 4, characterized in that: The final section of the flushing fluid channel (9) is located on the pressure ring platform (8b), thereby making the flushing fluid entering the flushing fluid cavity (7) apply more even pressure to both ends of the pressure ring platform (8b).

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