Oil seals and screw compressors

Abstract

This invention relates to the field of screw compressor technology, and discloses an oil sealing device and a screw compressor. The oil sealing device is mounted on the rotor's drive shaft, located between the drive gear and the bushing. The oil sealing device includes a bimetallic ring positioned near the drive gear and a sealing ring seat positioned near the bushing. The sealing ring seat has a raised ring. When the bimetallic ring is not deformed, it is tightly fitted. When the bimetallic ring deforms, it bends towards the drive gear, creating a gap between the bimetallic ring and the raised ring. An oil storage space is also provided between the bimetallic ring and the sealing ring seat, capable of storing oil and communicating with the gap between the drive shaft and the bushing. By employing the above technical solution, the screw compressor can avoid oil leakage and ensure sufficient oil, guaranteeing lubrication. It also ensures the uniformity of the overall oil particle size, preventing metal debris from accumulating only in the oil storage space.

Description

Technical Field

[0001] This invention relates to the field of screw compressor technology, and more specifically to an oil sealing device and a screw compressor. Background Technology

[0002] Screw compressors are widely used rotary compressors, belonging to the category of positive displacement compressors. They are characterized by their ability to operate at relatively low pressures with a wide flow range. In petrochemical production, they are frequently used for natural gas gathering and transportation, fuel gas pressurization, refrigeration, compression (propane / butane), flare gas compression, and air compression. Screw compressors are divided into single-screw compressors and twin-screw compressors. The single-screw compressor was developed in the 1970s by Sinn, France. Due to its more rational structure, it was quickly adopted in the defense field and protected by developing countries, with the technology remaining relatively independent. The twin-screw compressor was first proposed by H. Krigar of Germany in 1878, but it wasn't until 1934 that A. Lysholm of the Royal Institute of Technology in Sweden established the SRM (Screw Refrigerant Regulator) technology for screw compressors, leading to its rapid industrial application and development.

[0003] Oil leakage is prone to occur in existing screw compressors. This is because when the compressor is started in a cold state, the gap between the rotor and the bushing is large, and the oil pressure in the gear chamber suddenly increases. The resulting pulse enters the larger gap, thus causing oil leakage. Summary of the Invention

[0004] The purpose of this invention is to provide an oil sealing device and a screw compressor, which can solve the problem of easy oil leakage in the prior art.

[0005] To achieve the above objectives, a first aspect of the present invention provides an oil sealing device disposed on the drive shaft of a rotor, located between the drive gear and the bushing. The oil sealing device includes a bimetallic ring disposed near the drive gear and a sealing ring seat disposed near the bushing. The sealing ring seat has a raised ring. When the bimetallic ring is not deformed, the bimetallic ring is tightly attached. When the bimetallic ring is deformed, it bends towards the drive gear, and a gap is formed between the bimetallic ring and the raised ring. An oil storage space capable of storing oil and communicating with the gap between the drive shaft and the bushing is also provided between the bimetallic ring and the sealing ring seat.

[0006] The screw compressor, utilizing the aforementioned technical solution, ensures that during cold starts, the raised ring and bimetallic ring are tightly fitted, isolating the oil reservoir from the external oil. The oil pulse fluctuations during startup do not affect the oil reservoir, meaning the oil will not impact the gap between the drive shaft and bushing, preventing oil leakage. Furthermore, the oil reservoir can replenish the oil in the gap between the drive shaft and bushing, ensuring sufficient oil and effective lubrication. As the oil temperature gradually rises, the bimetallic ring bends, opening the gap with the raised ring. At this point, the overall temperature has increased, and the gap between the drive shaft and bushing decreases due to thermal expansion and contraction, allowing the oil reservoir to circulate with the external oil. This ensures uniform oil particle size and prevents metal debris from accumulating solely within the oil reservoir.

[0007] Furthermore, the sealing ring seat is fixedly installed, and the bimetallic ring rotates relative to the drive shaft.

[0008] Furthermore, the end of the sealing ring seat away from the protruding ring is embedded between the bushing and the drive shaft support seat, and a plurality of positioning blocks are provided at intervals in the middle of the sealing ring seat, which are embedded in the end face of the drive shaft support seat.

[0009] Furthermore, the bimetallic ring is connected to the drive shaft via a bearing.

[0010] Furthermore, the bimetallic ring is provided with a plurality of limiting blocks at intervals near the sealing ring seat, and the sealing ring seat is provided with a plurality of grooves at intervals on the end side that can be embedded in the limiting blocks.

[0011] Furthermore, when the bimetallic ring deforms, the limiting block moves away from the groove.

[0012] A second aspect of the present invention provides a screw compressor, including the aforementioned oil sealing device.

[0013] With the above technical solution, during cold starts, the raised ring and bimetallic ring are tightly fitted, isolating the oil reservoir from the external oil. The oil pulse fluctuations during startup will not affect the oil reservoir, meaning the oil will not impact the gap between the drive shaft and bushing, preventing oil leakage. Furthermore, the oil reservoir can replenish the oil in the gap between the drive shaft and bushing, ensuring sufficient oil and guaranteeing lubrication. As the oil temperature gradually rises, the bimetallic ring bends, opening the gap between itself and the raised ring. At this point, the overall temperature has increased, and the gap between the drive shaft and bushing decreases due to thermal expansion and contraction, allowing the oil reservoir to circulate with the external oil. This ensures uniform oil particle size and prevents metal debris from accumulating solely within the oil reservoir.

[0014] Furthermore, the screw compressor also includes a housing, a partition, a rotor cavity, a gear cavity, a male rotor, a female rotor, a first drive gear, a second drive gear, a pulley, and a bushing. The partition divides the internal space of the housing into a rotor cavity and a gear cavity. Two meshing male and female rotors are arranged in the rotor cavity. The drive shafts of the male and female rotors pass through the gear cavity and are respectively connected to the first drive gear and the second drive gear. The first drive gear and the second drive gear mesh with each other. A pulley is arranged at the distal end of the male rotor. The bushing is arranged in the drive shaft support seat of the partition to support the drive shaft. The oil sealing device is arranged on the drive shaft of the rotor, located between the drive gear and the bushing.

[0015] Furthermore, both the first drive gear and the second drive gear are provided with recesses.

[0016] Furthermore, both the male rotor and the female rotor are equipped with an oil sealing device on their drive shafts.

[0017] Other features and advantages of the present invention will be described in detail in the following detailed description section. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of a specific embodiment of the oil sealing device of the present invention;

[0019] Figure 2 This is a schematic diagram of a specific embodiment of the screw compressor of the present invention.

[0020] Explanation of reference numerals in the attached figures

[0021] Rotor 11, male rotor 111, female rotor 112, drive shaft 12, drive gear 13, first drive gear 131, second drive gear 132, recess 133, bushing 14, drive shaft support seat 15, bimetallic ring 2, limiting block 21, sealing ring seat 3, raised ring 31, positioning block 32, groove 33, oil storage space 4, bearing 6, housing 51, partition 52, rotor cavity 53, gear cavity 54, pulley 55. Detailed Implementation

[0022] The following provides a detailed description of specific embodiments of the present invention. It should be understood that the specific embodiments described herein are for illustrative and explanatory purposes only and are not intended to limit the scope of the invention.

[0023] In this invention, unless otherwise stated, directional terms such as "upper" and "lower" generally refer to the orientation in the assembled and used state. "Inner" and "outer" refer to the inner and outer sides relative to the outline of each component itself.

[0024] To solve the aforementioned technical problems that easily lead to oil leakage, such as Figure 2 As shown, the first aspect of the present invention provides an oil sealing device, which is disposed on the drive shaft 12 of the rotor 11, located between the drive gear 13 and the bushing 14. The oil sealing device includes a bimetallic ring 2 disposed near the drive gear 13 and a sealing ring seat 3 disposed near the bushing 14. The sealing ring seat 3 has a raised ring 31. When the bimetallic ring 2 is not deformed, the bimetallic ring 2 is tightly attached. When the bimetallic ring 2 is deformed, it bends towards the drive gear 13, and a gap is created between the bimetallic ring 2 and the raised ring 31. An oil storage space 4 is also provided between the bimetallic ring 2 and the sealing ring seat 3, which can store oil and connects the gap between the drive shaft 12 and the bushing 14. With the above technical solution, the screw compressor, during cold start, has the raised ring 31 tightly attached to the bimetallic ring 2, isolating the oil storage space 4 from the external oil. The oil pulse fluctuations during start-up will not affect the oil storage space 4, that is, the oil will not impact the gap between the drive shaft 12 and the bushing 14, thus avoiding oil leakage. Furthermore, the oil reservoir 4 can replenish the oil in the gap between the drive shaft 12 and the bushing 14, ensuring sufficient oil and guaranteeing lubrication. As the oil temperature gradually rises, the bimetallic ring 2 bends, opening the gap between itself and the raised ring 31. At this time, the overall temperature has increased, and the gap between the drive shaft 12 and the bushing 14 decreases due to thermal expansion and contraction, allowing the oil reservoir 4 to circulate with the external oil, ensuring the uniformity of the overall oil particle size and preventing metal debris from accumulating solely within the oil reservoir 4.

[0025] To reduce wear between the bimetallic ring 2 and the drive gear 13, in a preferred embodiment, the sealing ring seat 3 is fixedly installed, and the bimetallic ring 2 rotates relative to the drive shaft 12. Specifically, the end of the sealing ring seat 3 away from the protruding ring 31 is embedded between the bushing 14 and the drive shaft support 15, and the sealing ring seat 3 is provided with multiple positioning blocks 32 at intervals in the middle, which are embedded in the end face of the drive shaft support 15. The bimetallic ring 2 and the drive shaft 12 are connected by a bearing 6. The bimetallic ring 2 can rotate with the drive gear 13, thereby reducing wear.

[0026] To reduce wear between the bimetallic ring 2 and the raised ring 31 caused by the rotation of the bimetallic ring 2, which could further reduce the sealing effect, in a preferred embodiment, multiple limiting blocks 21 are spaced apart near the sealing ring seat 3, and multiple grooves 33 that can be inserted into the limiting blocks 21 are correspondingly spaced apart on the side of the end of the sealing ring seat 3. When the bimetallic ring 2 is not deformed, the limiting blocks 21 are inserted into the grooves 33, and the bimetallic ring 2 and the sealing ring seat 3 are circumferentially fixed. At this time, when the compressor is started cold, on the one hand, the gap between the bimetallic ring 2 and the drive gear 13 is large, and the two are not prone to wear; on the other hand, the circumferential fixation of the bimetallic ring 2 and the sealing ring seat 3 can improve the sealing performance at this time and avoid pulses in the oil during cold start. When the bimetallic ring 2 is deformed, the limiting blocks 21 leave the grooves 33, and the gap between the bimetallic ring 2 and the drive gear 13 becomes smaller due to the increase in ambient temperature, making them prone to wear. Allowing the bimetallic ring 2 to follow the drive gear 13 can reduce the wear between the two.

[0027] like Figure 1 As shown, a second aspect of the present invention provides a screw compressor, including the aforementioned oil sealing device. Through the above technical solution, during cold start-up, the raised ring 31 is tightly attached to the bimetallic ring 2, isolating the oil storage space 4 from the external oil. The oil pulse fluctuations during start-up will not affect the oil storage space 4, meaning the oil will not impact the gap between the drive shaft 12 and the bushing 14, preventing oil leakage. Furthermore, the oil storage space 4 can replenish the oil in the gap between the drive shaft 12 and the bushing 14, ensuring sufficient oil and guaranteeing lubrication. As the oil temperature gradually increases, the bimetallic ring 2 bends, opening the gap with the raised ring 31. At this time, the overall temperature has increased, and the gap between the drive shaft 12 and the bushing 14 decreases due to thermal expansion and contraction, allowing the oil storage space 4 to circulate with the external oil, ensuring the uniformity of the overall oil particle size and preventing metal debris from accumulating solely within the oil storage space 4.

[0028] To reduce wear between the male rotor 111 and the female rotor 112, in a preferred embodiment, the screw compressor further includes a housing 51, a partition 52, a rotor cavity 53, a gear cavity 54, a male rotor 111, a female rotor 112, a first drive gear 131, a second drive gear 132, a pulley 55, and a bushing 14. The partition 52 divides the internal space of the housing 51 into the rotor cavity 53 and the gear cavity 54. Two meshing male rotors 111 and female rotors 112 are disposed within the rotor cavity 53. The drive shafts 12 of the male rotor 111 and female rotor 112 pass through the gear cavity 54 and are respectively connected to the first drive gear 131 and the second drive gear 132. The first drive gear 131 and the second drive gear 132 mesh with each other. A pulley 55 is provided at the distal end of the male rotor 111. The bushing 14 is provided in the drive shaft support seat 15 of the partition plate 52 to support the drive shaft 12. The oil sealing device is provided on the drive shaft 12 of the rotor 11, located between the drive gear 131 and the bushing 14. The gear cavity 54 is filled with oil. Through the meshing of the first drive gear 131 and the second drive gear 132, the male rotor 111 drives the female rotor 112 to rotate simultaneously, so that the two can maintain the same speed and the meshing posture of the two can maintain a stable state, which can reduce the impact of the male rotor 111 on the female rotor 112.

[0029] To provide sufficient free space for the deformation of the bimetallic ring 2, in a preferred embodiment, both the first drive gear 131 and the second drive gear 132 are provided with recesses 133. When the bimetallic ring 2 deforms, it bends towards the recesses 133, preventing the end of the bimetallic ring 2 from contacting the first drive gear 131 and the second drive gear 132.

[0030] To ensure consistent sealing of the drive shafts 12 of the male rotor 111 and the female rotor 112, in a preferred embodiment, both the drive shafts 12 of the male rotor 111 and the female rotor 112 are equipped with an oil sealing device.

[0031] The preferred embodiments of the present invention have been described in detail above. However, the present invention is not limited to the specific details in the above embodiments. Within the scope of the technical concept of the present invention, various simple modifications can be made to the technical solution of the present invention, and these simple modifications all fall within the protection scope of the present invention.

[0032] It should also be noted that the various specific technical features described in the above embodiments can be combined in any suitable manner without contradiction. To avoid unnecessary repetition, the present invention will not describe the various possible combinations separately.

[0033] Furthermore, various different embodiments of the present invention can be combined in any way, as long as they do not violate the spirit of the present invention, they should also be regarded as the content disclosed by the present invention.

Claims

1. A screw compressor, characterized in that, The screw compressor, including an oil sealing device, also includes a housing (51), a partition (52), a rotor cavity (53), a gear cavity (54), a male rotor (111), a female rotor (112), a first drive gear (131), a second drive gear (132), a pulley (55), and a bushing (14). The partition (52) divides the internal space of the housing (51) into a rotor cavity (53) and a gear cavity (54). Two meshing male rotors (111) and female rotors (112) are arranged in the rotor cavity (53). The drive shafts (12) of the male rotors (111) and female rotors (112) pass through the gear cavity (54) and are respectively connected to the first drive gear (131) and the second drive gear (132). The wheel (131) and the second drive gear (132) mesh with each other. A pulley (55) is provided at the far end of the male rotor (111). The bushing (14) is provided in the drive shaft support seat (15) of the partition plate (52) to support the drive shaft (12). The oil sealing device is provided on the drive shaft (12) of the rotor (11) and is located between the drive gear (13) and the bushing (14). The oil sealing device includes a bimetallic ring (2) provided near the drive gear (13) and a sealing ring seat (3) provided near the bushing (14). The sealing ring seat (3) has a raised ring (31). An oil storage space (4) is also provided between the bimetallic ring (2) and the sealing ring seat (3) to store oil and to connect the gap between the drive shaft (12) and the bushing (14). During cold start, the raised ring (31) and the bimetallic ring (2) are in close contact, isolating the oil storage space (4) from the oil outside, and the oil storage space (4) can replenish the oil in the gap between the drive shaft (12) and the bushing (14); as the oil temperature gradually rises, the bimetallic ring (2) bends towards the drive gear (13), opening the gap between it and the raised ring (31), so that the oil storage space (4) circulates with the oil outside.

2. The screw compressor according to claim 1, characterized in that, Both the first drive gear (131) and the second drive gear (132) are provided with recesses (133).

3. The screw compressor according to claim 2, characterized in that, Both the male rotor (111) and the female rotor (112) are equipped with an oil sealing device on their drive shafts (12).

4. The screw compressor according to claim 1, characterized in that, The sealing ring seat (3) is fixedly installed, and the bimetallic ring (2) rotates relative to the drive shaft (12).

5. The screw compressor according to claim 4, characterized in that, The sealing ring seat (3) is embedded between the bushing (14) and the drive shaft support seat (15) at one end away from the protruding ring (31). The sealing ring seat (3) is provided with a plurality of positioning blocks (32) that are embedded in the end face of the drive shaft support seat (15) at intervals in the middle.

6. The screw compressor according to claim 4, characterized in that, The bimetallic ring (2) is connected to the drive shaft (12) via a bearing (6).

7. The screw compressor according to claim 6, characterized in that, The bimetallic ring (2) is provided with a plurality of limiting blocks (21) at intervals near the sealing ring seat (3), and the sealing ring seat (3) is provided with a plurality of grooves (33) at intervals on the side of the end of the sealing ring seat (3) that can be embedded in the limiting blocks (21).

8. The screw compressor according to claim 7, characterized in that, When the bimetallic ring (2) deforms, the limiting block (21) leaves the groove (33).

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