Rotor supporting layout applied to oil injection screw compressor
By combining oil pressure self-balancing and mechanical balancing rotor support layout in oil-injected screw compressors, the problem of unbalanced axial force of traditional screw compressor rotors is solved, achieving the effects of reducing vibration and lowering costs.
Patent Information
- Application Number
- CN202520006407.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-01-03
- Publication Date
- 2025-12-19
- Estimated Expiration
- 2035-01-03
AI Technical Summary
The rotor support layout of traditional screw compressors leads to an imbalance of axial forces, resulting in vibration and component damage. Existing layouts are complex and costly.
The rotor support layout combines hydraulic self-balancing and mechanical balancing. By installing dynamic pressure bearings and rolling bearings at both ends of the rotor, and utilizing the pressure difference between the high-pressure oil of the oil-injected screw compressor and the intake air pressure, self-balancing is achieved, reducing the number of bearings and vibration.
It effectively reduces vibration during operation, lowers costs, and improves the stability of the rotor support layout and the service life of the bearings.
Smart Images
Figure CN223689943U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model relates to screw compressor technical field especially relates to a rotor support layout for oil injection screw compressor. BACKGROUND
[0002] Screw compressor is a kind of positive displacement compressor widely used in industrial field, and its core component is a pair of mutually meshing female rotor and male rotor. The support layout of rotor directly affects the efficiency, stability and service life of compressor, and the support layout of rotor of screw compressor mainly involves the axial and radial force balance of rotor.
[0003] In traditional screw compressor, rotor usually only inhales air at one end and exhausts at the other end, resulting in that rotor bears axial force in single direction in axial direction, which may cause damage to compressor components, is not conducive to long-term operation of machine, and the axial and radial force balance of rotor needs to be comprehensively considered to ensure that bearing and related components can effectively bear load and maintain stability during operation.
[0004] In different application occasions, the axial force of gas in compressor on rotor is different, and the main factors affecting the force of rotor include compression medium, suction pressure, exhaust pressure, rotational speed, profile line, etc. When suction pressure is certain, the greater the exhaust pressure, the greater the force value of rotor, and if the exhaust pressure is smaller, the smaller the force value of rotor.
[0005] The existing rotor support layout usually arranges several bearings at both ends of female rotor and male rotor to bear axial force and radial force of rotor, and only arranges bearings according to maximum bearing force, which is high in cost and complex in layout structure. UTILITY MODEL CONTENTS
[0006] The utility model aims at providing a rotor support layout for oil injection screw compressor, which can effectively reduce vibration during operation.
[0007] The technical scheme of the utility model is as follows: a rotor support layout for oil injection screw compressor, comprising female rotor and male rotor arranged in compressor and mutually meshing, both ends of female rotor and male rotor are provided with dynamic pressure bearing assembly for bearing radial load, one end of female rotor and male rotor is provided with rolling bearing assembly for bearing axial load, and the other end of female rotor and male rotor is provided with oil pressure self-balancing mechanism for balancing axial load.
[0008] Further, the dynamic pressure bearing assembly comprises first radial liquid dynamic pressure bearing mounted on first stepped shaft at one end of female rotor and male rotor, and second radial liquid dynamic pressure bearing is mounted on first stepped shaft at the other end of female rotor and male rotor.
[0009] Further, the first radial hydrodynamic pressure bearing has a gap between the shaft shoulder of the first stepped shaft at one end of the female rotor and the shaft shoulder of the first stepped shaft at one end of the male rotor.
[0010] Further, the rolling bearing assembly comprises a first axial rolling bearing mounted on the second stepped shaft at one end of the female rotor, a second axial rolling bearing mounted on the fourth stepped shaft at one end of the female rotor, a third axial rolling bearing mounted on the second stepped shaft at one end of the male rotor, and a fourth axial rolling bearing mounted on the third stepped shaft at one end of the male rotor.
[0011] Further, the first axial rolling bearing has a gap between the shaft shoulder of the second stepped shaft at one end of the female rotor, and the third axial rolling bearing has a gap between the shaft shoulder of the second stepped shaft at one end of the male rotor.
[0012] Further, the oil pressure self-balancing mechanism comprises a first balancing piston mounted on the second stepped shaft at the other end of the female rotor, and a second balancing piston mounted on the second stepped shaft at the other end of the male rotor.
[0013] Further, the compressor is further provided with an oil supply mechanism for supplying oil to the hydrodynamic pressure bearing assembly and the oil pressure self-balancing mechanism.
[0014] Further, the oil supply mechanism comprises an oil supply main pipeline, and a piston branch pipeline leading to the oil pressure self-balancing mechanism and a bearing branch pipeline leading to the hydrodynamic pressure bearing assembly are arranged on the oil supply main pipeline.
[0015] Compared with the prior art, the utility model has the following advantages:
[0016] 1. The rotor support layout adopts the combination of oil pressure self-balancing and mechanical balancing, that is, on the basis of reasonable arrangement of bearings, an oil pressure self-balancing mechanism is added. The oil pressure self-balancing refers to the use of the pressure difference between the high-pressure oil generated by the oil injection screw compressor itself and the intake pressure to reasonably use the balancing mechanism to offset a part of rotor shaft force. The mechanical balancing refers to the arrangement of bearings, the arrangement of radial hydrodynamic pressure bearings, the use of oil pressure lubrication support, and the realization of self-balancing, and the arrangement of axial rolling bearings to bear axial load.
[0017] 2. The rotor support layout structure is simple, has strong universality, can adapt to different working conditions, effectively reduces vibration during operation, reduces the number of bearings used, and has relatively low cost. BRIEF DESCRIPTION OF DRAWINGS
[0018] Figure 1 It is a structural schematic view of the utility model;
[0019] In the figure: 1 - female rotor, 2 - male rotor, 3 - first radial liquid dynamic pressure bearing, 4 - first radial liquid dynamic pressure bearing, 5 - second radial liquid dynamic pressure bearing, 6 - second radial liquid dynamic pressure bearing, 7 - first axial rolling bearing, 8 - second axial rolling bearing, 9 - third axial rolling bearing, 10 - fourth axial rolling bearing, 11 - first balance piston, 12 - second balance piston, 13 - oil supply main line, 14 - first branch, 15 - second branch, 16 - third branch, 17 - fourth branch, 18 - fifth branch, 19 - sixth branch, 20 - seventh branch. DETAILED DESCRIPTION
[0020] In order to make the above features and advantages of the utility model more obvious, the following specific examples are given, and the detailed description is given as follows by combining with the drawings, but the utility model is not limited to this.
[0021] REFERENCE Figure 1
[0022] A rotor support layout applied to an oil-injected screw compressor, comprising a female rotor 1 and a male rotor 2 arranged in the compressor and meshing with each other, the female rotor and the male rotor are both provided with a dynamic pressure bearing assembly for bearing radial load, one end of the female rotor and the male rotor is provided with a rolling bearing assembly for bearing axial load, and the other end of the female rotor and the male rotor is provided with an oil pressure self-balancing mechanism for balancing axial load. The oil pressure self-balancing and mechanical balancing are combined, that is, on the basis of reasonable arrangement of the bearing, the oil pressure self-balancing mechanism is added, which can effectively reduce the vibration in the operation process and reduce the number of bearings used.
[0023] The mechanical balance refers to the arrangement of the bearing, the radial liquid dynamic pressure bearing is arranged, the oil pressure lubrication support is used, and then the self-balancing is realized, and the axial rolling bearing is arranged to bear the axial load.
[0024] Specifically, the dynamic pressure bearing assembly comprises first radial liquid dynamic pressure bearings 3 and 4 mounted on first stepped shafts at right ends of the female rotor and the male rotor respectively, and second radial liquid dynamic pressure bearings 5 and 6 are mounted on the first stepped shafts at the right ends of the female rotor and the male rotor respectively. The load is borne by the first radial liquid dynamic pressure bearings and the second radial liquid dynamic pressure bearings. Since the radial liquid dynamic pressure bearing is a bearing working under sliding friction, an oil film can be formed between the bearing bush and the shaft neck to bear the load applied by the shaft neck, thereby reducing wear and heat generation.
[0025] The radial liquid dynamic pressure bearing also has the function of self-balancing: high-pressure oil flows into the first radial liquid dynamic pressure bearings and the second radial liquid dynamic pressure bearings respectively, the higher the oil pressure injected into the bearing, the stronger the bearing capacity of the bearing.
[0026] In the embodiment, the first radial liquid dynamic pressure bearing has a gap between the shaft shoulder of the first stepped shaft at the right end of the female rotor and the shaft shoulder of the first stepped shaft at the right end of the male rotor, so as to provide space for axial movement of the female rotor and the male rotor.
[0027] In the embodiment, the rolling bearing assembly comprises a first axial rolling bearing 7 mounted on the second stepped shaft at the right end of the female rotor, a second axial rolling bearing 8 mounted on the fourth stepped shaft at the right end of the female rotor, a third axial rolling bearing 9 mounted on the second stepped shaft at the right end of the male rotor, and a fourth axial rolling bearing 10 mounted on the third stepped shaft at the right end of the male rotor. Thus, the axial load of the female rotor is borne by the first axial rolling bearing and the second axial rolling bearing, and the axial load of the male rotor is borne by the third axial rolling bearing and the fourth axial rolling bearing.
[0028] In the embodiment, the first axial rolling bearing has a gap between the shaft shoulder of the second stepped shaft at the right end of the female rotor, and the first axial rolling bearing abuts against the corresponding first radial liquid dynamic pressure bearing 3 on the female rotor. The third axial rolling bearing has a gap between the shaft shoulder of the second stepped shaft at the right end of the male rotor, and the third axial rolling bearing abuts against the corresponding first radial liquid dynamic pressure bearing 4 on the male rotor. The gaps provide space for axial movement of the female rotor and the male rotor.
[0029] The oil pressure self-balancing refers to using the pressure difference between the high-pressure oil generated by the oil injection screw compressor itself and the intake pressure, reasonably using the balancing mechanism, and offsetting part of the rotor shaft force by the force generated by the pressure difference.
[0030] In the embodiment, the oil pressure self-balancing mechanism comprises a first balancing piston 11 mounted on the second stepped shaft at the left end of the female rotor, and a second balancing piston 12 mounted on the second stepped shaft at the left end of the male rotor.
[0031] In the embodiment, the compressor is further provided with an oil supply mechanism for supplying oil to the dynamic pressure bearing assembly and the oil pressure self-balancing mechanism. The oil supply mechanism comprises an oil supply main pipeline 13, and the oil supply main pipeline is provided with a piston branch pipeline leading to the oil pressure self-balancing mechanism and a bearing branch pipeline leading to the dynamic pressure bearing assembly.
[0032] Specifically, the oil supply main pipeline 13 is provided with a first branch 14, the first branch is provided with a second branch 15 leading to the first balancing piston and a third branch 16 leading to the second balancing piston. The injected high-pressure oil forms a high-pressure area in the oil cavity, and a pressure difference is generated between the high-pressure area and the original low-pressure area in the compressor. Under the action of the pressure difference, an axial force in the direction from high pressure to low pressure is provided to balance the axial load. The oil pressure difference is generated by the operation of the compressor itself. The larger the pressure difference, the greater the force of the balancing piston, and the greater the offset force. The oil pressure difference can also be used to lubricate and cool the axial rolling bearing, thereby improving the service life of the axial rolling bearing.
[0033] The oil supply main pipe 13 is also provided with a fourth branch 17 leading to the second radial hydrodynamic pressure bearing of the left end of the female rotor, a fifth branch 18 leading to the first radial hydrodynamic pressure bearing of the right end of the female rotor, a sixth branch 19 leading to the second radial hydrodynamic pressure bearing of the left end of the male rotor, and a seventh branch 20 leading to the first radial hydrodynamic pressure bearing of the right end of the male rotor.
[0034] The above-mentioned "first", "second" and the like are used to limit the components, and those skilled in the art should know that: the use of "first", "second" is only for the convenience of distinguishing the components, and the above-mentioned words have no special meaning unless otherwise stated.
[0035] If the utility model discloses or involves mutually fixed and connected components or structural members, then, except for another declaration, the fixed connection can be understood as: detachably fixed connection (for example, bolt or screw connection), and can also be understood as: non-detachable fixed connection (for example, riveting, welding), of course, the mutual fixed connection can also be replaced by an integral structure (for example, integrally formed by using casting process) (except for obviously unable to use integral forming process).
[0036] In addition, the terms used to represent the positional relationship or shape in any of the above-mentioned utility model disclosed technical solutions include the approximate, similar or close state or shape unless otherwise stated.
[0037] Any component provided by the utility model can be assembled from a plurality of individual components, or can be a single component manufactured by integral forming process.
[0038] The above-mentioned is only the preferred embodiment of the utility model, and any change and modification made according to the patent application scope of the utility model shall belong to the coverage range of the utility model.
Claims
1. A rotor support layout applied to an oil-injected screw compressor, comprising a female rotor and a male rotor disposed in the compressor and engaged with each other, characterized in that, The two ends of the female rotor and the male rotor are provided with dynamic pressure bearing assemblies for bearing radial load, one end of the female rotor and the male rotor is provided with a rolling bearing assembly for bearing axial load, and the other end of the female rotor and the male rotor is provided with an oil pressure self-balancing mechanism for balancing axial load.
2. A rotor support arrangement for use in an oil-injected screw compressor as claimed in claim 1, characterized in that The dynamic pressure bearing assembly comprises a first radial liquid dynamic pressure bearing mounted on a first stepped shaft at one end of the female rotor and the male rotor, and a second radial liquid dynamic pressure bearing mounted on a first stepped shaft at the other end of the female rotor and the male rotor.
3. A rotor support arrangement for use in an oil-injected screw compressor as claimed in claim 2, characterized in that The first radial liquid dynamic pressure bearing has a gap between the shaft shoulder of the first stepped shaft at one end of the female rotor and the male rotor.
4. A rotor support arrangement for use in an oil-injected screw compressor according to claim 1, 2 or 3, characterized in that The rolling bearing assembly comprises a first axial rolling bearing mounted on a second stepped shaft at one end of the female rotor, a second axial rolling bearing mounted on a fourth stepped shaft at one end of the female rotor, a third axial rolling bearing mounted on a second stepped shaft at one end of the male rotor, and a fourth axial rolling bearing mounted on a third stepped shaft at one end of the male rotor.
5. A rotor support arrangement for use in an oil-injected screw compressor as claimed in claim 4, characterized in that The first axial rolling bearing has a gap between the shaft shoulder of the second stepped shaft at one end of the female rotor, and the third axial rolling bearing has a gap between the shaft shoulder of the second stepped shaft at one end of the male rotor.
6. A rotor support arrangement for use in an oil-injected screw compressor according to claim 1, 2, 3 or 5, characterized in that The oil pressure self-balancing mechanism comprises a first balancing piston mounted on a second stepped shaft at the other end of the female rotor, and a second balancing piston mounted on a second stepped shaft at the other end of the male rotor.
7. A rotor support arrangement for use in an oil-injected screw compressor according to claim 1, 2, 3 or 5, characterized in that The compressor is further provided with an oil supply mechanism for supplying oil to the dynamic pressure bearing assembly and the oil pressure self-balancing mechanism.
8. A rotor support arrangement for use in an oil-injected screw compressor according to claim 7, characterized in that The oil supply mechanism comprises an oil supply main pipeline, and a piston branch pipeline leading to the oil pressure self-balancing mechanism and a bearing branch pipeline leading to the dynamic pressure bearing assembly are arranged on the oil supply main pipeline.