Oil seal device and screw compressor

Abstract

The present invention relates to the technical field of screw compressors, and discloses an oil sealing device and a screw compressor. Among them, the oil sealing device is arranged on the drive shaft of the rotor, between the drive gear and the bushing. The bushing is sleeved in the drive shaft support seat. The oil sealing device includes a bimetallic ring fixedly arranged on the drive gear, an annular groove arranged on the end face of the drive shaft support seat, and a bearing arranged in the annular groove. When the bimetallic ring is not deformed, the bimetallic ring is in close contact with the side wall of the bearing; when the bimetallic ring is deformed, it bends towards the drive gear, and a gap is generated between the bimetallic ring and the bearing; there is also an oil storage space capable of storing oil and communicating with the gap between the drive shaft and the bushing arranged among the bimetallic ring, the drive gear, and the drive shaft support seat. With the above technical solution, oil leakage is avoided and the lubrication effect is ensured.

Description

Technical Field

[0001] The present invention relates to the technical field of screw compressors, and particularly to an oil sealing device and a screw compressor. Background Art

[0002] Screw compressors are rotary compressors with a relatively wide range of uses and belong to a type of positive displacement compressor. It has the operating characteristics of a relatively wide flow range at a relatively low pressure. In petrochemical production, it is often used in natural gas gathering and transportation, fuel gas boosting, 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 by Sinn in France in the 1970s. Due to its more reasonable structure, it was quickly applied to the national defense field and protected by the developed countries, and the technology has been relatively independent. The twin-screw compressor was first proposed by the German H. Krigar in 1878. It was not until 1934 that A. Lysholm of the Royal Institute of Technology in Sweden established the SRM technology of screw compressors and began to be applied industrially, achieving rapid development.

[0003] In existing screw compressors, oil leakage is likely to occur. The reason is that when the compressor is started in a cold machine state, the gap between the rotor and the bushing is relatively large at this time, the oil pressure in the gear chamber suddenly rises, and the generated pulse enters the larger gap, resulting in oil leakage. Summary of the Invention

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

[0005] To achieve the above object, in a first aspect of the present invention, an oil sealing device is provided, which is arranged on the drive shaft of the rotor and is located between the drive gear and the bushing. The bushing is sleeved in the drive shaft support seat. The oil sealing device includes a bimetallic ring fixedly arranged on the drive gear, an annular groove arranged on the end face of the drive shaft support seat, and a bearing arranged in the annular groove. When the bimetallic ring is not deformed, the bimetallic ring is in close contact with the side wall of the bearing; when the bimetallic ring is deformed, it bends towards the drive gear, and a gap is generated between the bimetallic ring and the bearing; a storage space capable of storing oil and communicating with the gap between the drive shaft and the bushing is further arranged among the bimetallic ring, the drive gear, and the drive shaft support seat.

[0006] With the above technical solution of the screw compressor, during cold start, the bimetallic ring is in close contact with the bearing, isolating the oil storage space from the engine oil outside. The oil pulse fluctuations during startup will not affect the oil storage space, that is, the engine oil will not impact the gap between the drive shaft and the bushing, avoiding oil leakage. Moreover, the oil storage space can supplement the engine oil in the gap between the drive shaft and the bushing, ensuring sufficient engine oil and lubrication effect. After the engine oil temperature gradually rises, the bimetallic ring bends, opening the gap with the bearing. At this time, the overall temperature has risen, and the gap between the drive shaft and the bushing decreases under the action of thermal expansion and contraction, enabling the oil storage space to circulate with the engine oil outside, ensuring the uniformity of the overall particle size of the engine oil and preventing metal debris from accumulating only in the oil storage space. The function of setting the bearing is to make the bearing rotate with the bimetallic ring, thereby reducing the wear between the two.

[0007] Further, the bimetallic ring extends from the drive gear towards the drive shaft.

[0008] Further, when the bimetallic ring is not deformed, the bimetallic ring inclines towards the bearing.

[0009] Further, a first protrusion is provided at one end of the bimetallic ring close to the bearing. When the bimetallic ring is not deformed, the first protrusion rests on the circumferential surface of the bearing.

[0010] Further, a second protrusion extends from one end of the bimetallic ring close to the bearing in the opposite direction of the first protrusion. A fixing block is provided on the drive gear. When the bimetallic ring deforms, under the centrifugal force generated by the rotation of the drive gear, the second protrusion rests on the fixing block.

[0011] Further, the bimetallic ring extends from the drive gear away from the drive shaft.

[0012] The second aspect of the present invention provides a screw compressor including the above oil seal device.

[0013] With the above - described technical solution of the screw compressor, during cold - start, the bimetallic ring is in close contact with the bearing, isolating the oil storage space from the engine oil outside. The oil pulse fluctuations during startup will not affect the oil storage space. That is to say, the engine oil will not impact the gap between the drive shaft and the bushing, avoiding oil leakage. And the oil storage space can supplement the engine oil in the gap between the drive shaft and the bushing, ensuring sufficient engine oil and lubrication effect. After the engine oil temperature gradually rises, the bimetallic ring bends, opening the gap with the bearing. At this time, the overall temperature has risen, and the gap between the drive shaft and the bushing decreases under the action of thermal expansion and contraction, enabling the oil storage space to circulate with the engine oil outside, ensuring the uniformity of the overall particle size of the engine oil and preventing metal debris from accumulating only in the oil storage space. The function of setting the bearing is to make the bearing rotate with the bimetallic ring, thereby reducing the wear between the two.

[0014] Further, the screw compressor further includes a housing, a partition plate, a rotor chamber, a gear chamber, a male rotor, a female rotor, a first driving gear, a second driving gear, a pulley, and a bushing. The partition plate divides the internal space of the housing into a rotor chamber and a gear chamber. Two meshing male and female rotors are arranged in the rotor chamber. The drive shafts of the male and female rotors penetrate into the gear chamber and are respectively connected with a first driving gear and a second driving gear. The first driving gear and the second driving 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 plate for supporting the drive shaft. The oil - seal device is arranged on the drive shaft of the rotor, between the driving gear and the bushing.

[0015] Further, depressions are arranged on both the first driving gear and the second driving gear.

[0016] Further, oil - seal devices are arranged on the drive shafts of both the male rotor and the female rotor.

[0017] Other features and advantages of the present invention will be described in detail in the subsequent detailed implementation section. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a schematic structural diagram of a specific embodiment of the oil - seal device of the present invention;

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

[0020] DESCRIPTION OF THE REFERENCE NUMERALS

[0021] Rotator 11, male rotator 111, female rotator 112, drive shaft 12, drive gear 13, first drive gear 131, second drive gear 132, depression 133, bushing 14, drive shaft support seat 15, bimetallic ring 2, first protrusion 21, second protrusion 22, fixing block 23, support wall 24, mounting seat 25, bearing 3, oil storage space 4, housing 51, partition 52, rotator cavity 53, gear cavity 54, pulley 55. Detailed implementation mode

[0022] The following provides a detailed description of the specific implementation modes of the present invention. It should be understood that the specific implementation modes described herein are only used to illustrate and explain the present invention, and are not used to limit the present invention.

[0023] In the present invention, unless otherwise stated, the orientation 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 of the contour of each component itself.

[0024] In order to solve the above-mentioned technical problem of easy oil leakage, as Figure 2 shown, in the first aspect of the present invention, an engine oil sealing device is provided, which is arranged on the drive shaft 12 of the rotator 11, between the drive gear 13 and the bushing 14. The bushing 14 is sleeved in the drive shaft support seat 15. The engine oil sealing device includes a bimetallic ring 2 fixedly arranged on the drive gear 13, an annular groove arranged on the end face of the drive shaft support seat 15, and a bearing 3 arranged in the annular groove. When the bimetallic ring 2 is not deformed, the bimetallic ring 2 is in close contact with the side wall of the bearing 3. When the bimetallic ring 2 is deformed, it bends towards the drive gear 13, and a gap is generated between the bimetallic ring 2 and the bearing 3. An oil storage space 4 capable of storing oil and communicating with the gap between the drive shaft 12 and the bushing 14 is further arranged between the bimetallic ring 2, the drive gear 13 and the drive shaft support seat 15. With the above-mentioned technical solution of the screw compressor, when starting in the cold state, the bimetallic ring 2 is in close contact with the bearing 3, isolating the oil storage space 4 from the engine oil outside. The oil pulse fluctuation during startup will not affect the oil storage space 4, that is, the engine oil will not impact the gap between the drive shaft 12 and the bushing 14, avoiding oil leakage. And the oil storage space 4 can supplement the engine oil in the gap between the drive shaft 12 and the bushing 14, ensuring sufficient engine oil and lubrication effect. After the engine oil temperature gradually rises, the bimetallic ring 2 bends, opening the gap with the bearing 3. At this time, the overall temperature has risen, and the gap between the drive shaft 12 and the bushing 14 decreases under the action of thermal expansion and contraction, enabling the oil storage space 4 to circulate with the engine oil outside, ensuring the unity of the overall particle size of the engine oil and avoiding the accumulation of metal chips only in the oil storage space 4. The function of arranging the bearing 3 is to make the bearing 3 rotate with the bimetallic ring 2, thereby reducing the wear between the two.

[0025] Among them, the bearing 3 is in interference fit with the annular groove, reducing the gap between the bearing 3 and the annular groove during installation.

[0026] Among them, the bimetallic ring 2 bends when heated. Due to the different thermal expansion coefficients of each component layer, when the temperature changes, the deformation of the active layer is greater than that of the passive layer. As a result, the whole bimetallic sheet will bend towards the passive layer side, and then the curvature of this composite material changes to generate deformation.

[0027] As a first specific embodiment, the bimetallic ring 2 extends from the driving gear 13 towards the driving shaft 12.

[0028] Specifically, in order to increase the tightness of the fit between the bimetallic ring 2 and the bearing 3, when the bimetallic ring 2 is not deformed, the bimetallic ring 2 is inclined towards the bearing 3. Preferably, the range of the inclination angle a, that is, the angle formed by the bimetallic ring 2 and the plane where the diameter of the driving shaft 12 is located, is: 165° ≤ a < 180°. Through the setting of the above technical solution, the inclined bimetallic ring 2 rotates during cold start. Affected by the centrifugal force, it can be more closely attached to the bearing 3, so as to better relatively isolate the oil storage space 4 from the space outside it, reducing the pulsation in the engine oil during cold start.

[0029] Specifically, in order to make the bimetallic ring 2 fit more closely with the bearing 3, a first protrusion 21 is provided at one end of the bimetallic ring 2 close to the bearing 3. When the bimetallic ring 2 is not deformed, the first protrusion 21 rests on the circumferential surface of the bearing 3. Through the setting of the above technical solution, the contact area between the bimetallic ring 2 and the bearing 3 is increased. In addition, as Figure 2 shown, the first protrusion 21 is located on the inner wall of the bearing 3. Under the action of the centrifugal force, the first protrusion 21 can fit more closely with the inner wall of the bearing 3. Preferably, a corrosion-resistant rubber layer is provided on the bearing 3. This setting can increase the tightness between the first protrusion 21 and the bearing 3, and can also increase the friction force to make the followability of the bearing 3 better.

[0030] Specifically, after the bimetallic ring 2 is bent by heat, it will bend towards the driving wheel 13 side. The high-speed rotation of the driving shaft 12 generates centrifugal force, which will make the bimetallic ring 2 bend more. In order to prevent the bimetallic ring 2 from being damaged due to excessive bending, in a preferred case, a second protrusion 22 extends from the end of the bimetallic ring 2 close to the bearing 3 in the opposite direction of the first protrusion 21. A fixing block 23 is provided on the driving gear 13. When the bimetallic ring 2 is deformed, under the centrifugal force generated by the rotation of the driving gear 13, the second protrusion 22 rests on the fixing block 23.

[0031] The bimetallic ring 2 is fixedly connected to the drive gear 13 through the mounting seat 25. The mounting seat 25 is bolted to the side of the drive gear 13. It is cylindrical. A support wall 24 is provided at one end of the bimetallic ring 2 away from the bearing 3. The bimetallic ring 2 is in interference fit with the mounting seat 25. The support wall 24 increases the contact area between the bimetallic ring 2 and the mounting seat 25, ensuring reliable installation.

[0032] As another embodiment, the bimetallic ring 2 extends from the drive gear 13 in a direction away from the drive shaft 12. The difference between this embodiment and the previous one is that it is difficult to utilize the centrifugal force generated when the drive gear 13 rotates.

[0033] As Figure 1 shown, the second aspect of the present invention provides a screw compressor, including the oil sealing device described above. With the above technical solution set in the screw compressor, when starting in the cold state, the bimetallic ring 2 is in close contact with the bearing 3, isolating the oil storage space 4 from the oil outside it. The oil pulse fluctuations during startup 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, avoiding oil leakage. And the oil storage space 4 can supplement the oil in the gap between the drive shaft 12 and the bushing 14, ensuring sufficient oil and the lubrication effect. After the oil temperature gradually rises, the bimetallic ring 2 bends, opening the gap with the bearing 3. At this time, the overall temperature has risen, and the gap between the drive shaft 12 and the bushing 14 decreases under the action of thermal expansion and contraction, enabling the oil in the oil storage space 4 to circulate with the oil outside it, ensuring the unity of the overall particle size of the oil and preventing metal chips from accumulating only in the oil storage space 4. The function of providing the bearing 3 is to make the bearing 3 rotate with the bimetallic ring 2, thereby reducing the wear between the two.

[0034] In order to reduce the wear between the male rotor 111 and the female rotor 112, preferably, the screw compressor further includes a housing 51, a partition 52, a rotor chamber 53, a gear chamber 54, a male rotor 111, a female rotor 112, a first driving gear 131, a second driving gear 132, a pulley 55, and a bushing 14. The partition 52 divides the internal space of the housing 51 into a rotor chamber 53 and a gear chamber 54. Two meshing male rotor 111 and female rotor 112 are arranged in the rotor chamber 53. The drive shafts 12 of the male rotor 111 and the female rotor 112 penetrate into the gear chamber 54 and are respectively connected with a first driving gear 131 and a second driving gear 132. The first driving gear 131 and the second driving gear 132 mesh with each other. A pulley 55 is arranged at the distal end of the male rotor 111. The bushing 14 is arranged in the drive shaft support seat 15 of the partition 52 for supporting the drive shaft 12. The oil seal device is arranged on the drive shaft 12 of the rotor 11, between the driving gear 13 and the bushing 14. The gear chamber 54 is filled with oil. Through the meshing of the first driving gear 131 and the second driving gear 132, the male rotor 111 drives the female rotor 112 to rotate simultaneously with power, so that the two can maintain the same speed and the meshing posture of the two can remain stable, and the impact of the male rotor 111 on the female rotor 112 can be reduced.

[0035] In order to reduce the self-weight of the driving gears, depressions 133 are arranged on both the first driving gear 131 and the second driving gear 132.

[0036] In order to ensure the consistency of the sealing of the drive shafts 12 of the male rotor 111 and the female rotor 112, preferably, oil seal devices are arranged on the drive shafts 12 of the male rotor 111 and the female rotor 112.

[0037] 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 solutions of the present invention, and these simple modifications all belong to the protection scope of the present invention.

[0038] In addition, it should be noted that, among the various specific technical features described in the above specific embodiments, they can be combined in any suitable manner without conflict. In order to avoid unnecessary repetition, the present invention will not separately describe various possible combination methods.

[0039] In addition, any combination can be made between various different embodiments of the present invention as long as it does not violate the idea of the present invention, and it should also be regarded as the content disclosed by the present invention.

Claims

1. An engine oil sealing device, characterized in that, It is arranged on the drive shaft (12) of the rotor (11), between the drive gear (13) and the bushing (14). The bushing (14) is sleeved in the drive shaft support seat (15). The engine oil sealing device includes a bimetallic ring (2) fixedly arranged on the drive gear (13), an annular groove arranged on the end face of the drive shaft support seat (15), and a bearing (3) arranged in the annular groove. When the bimetallic ring (2) is not deformed, the bimetallic ring (2) is in close contact with the side wall of the bearing (3); when the bimetallic ring (2) is deformed, it bends towards the drive gear (13), and a gap is generated between the bimetallic ring (2) and the bearing (3); there is also an oil storage space (4) capable of storing oil and communicating with the gap between the drive shaft (12) and the bushing (14) arranged among the bimetallic ring (2), the drive gear (13), and the drive shaft support seat (15).

2. The oil seal device according to claim 1, characterized in that, The bimetallic ring (2) extends from the drive gear (13) towards the drive shaft (12).

3. The engine oil sealing device according to claim 2, characterized in that, When the bimetallic ring (2) is not deformed, the bimetallic ring (2) inclines towards the bearing (3).

4. The engine oil sealing device according to claim 2, wherein, One end of the bimetallic ring (2) close to the bearing (3) is provided with a first protrusion (21). When the bimetallic ring (2) is not deformed, the first protrusion (21) rests on the circumferential surface of the bearing (3).

5. The engine oil sealing device according to claim 4, wherein, One end of the bimetallic ring (2) close to the bearing (3) extends out a second protrusion (22) in the reverse direction of the first protrusion (21). A fixing block (23) is arranged on the drive gear (13). When the bimetallic ring (2) is deformed, under the centrifugal force generated by the rotation of the drive gear (13), the second protrusion (22) rests on the fixing block (23).

6. The engine oil sealing device according to claim 1, characterized in that The bimetallic ring (2) extends from the drive gear (13) away from the drive shaft (12).

7. A screw compressor, characterized in that, It includes the engine oil sealing device according to any one of claims 1-6.

8. The screw compressor according to claim 7, wherein, The screw compressor further includes a housing (51), a partition (52), a rotor chamber (53), a gear chamber (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 chamber (53) and a gear chamber (54). Two meshing male rotor (111) and female rotor (112) are arranged in the rotor chamber (53). The drive shafts (12) of the male rotor (111) and the female rotor (112) penetrate into the gear chamber (54) and are respectively connected with a first drive gear (131) and a second drive gear (132). The first drive gear (131) and the second drive gear (132) mesh with each other. A pulley (55) is arranged at the distal end of the male rotor (111). The bushing (14) is arranged in the drive shaft support seat (15) of the partition (52) to support the drive shaft (12). The engine oil sealing device is arranged on the drive shaft (12) of the rotor (11), between the drive gear (13) and the bushing (14).

9. The screw compressor according to claim 8, characterized in that, The first drive gear (131) and the second drive gear (132) are both provided with depressions (133).

10. The screw compressor according to claim 8, characterized in that, Oil sealing devices are provided on the drive shafts (12) of the male rotor (111) and the female rotor (112).

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