CN111120312A - Design method of screw compressor and screw compressor - Google Patents
Design method of screw compressor and screw compressor Download PDFInfo
- Publication number
- CN111120312A CN111120312A CN201911284878.1A CN201911284878A CN111120312A CN 111120312 A CN111120312 A CN 111120312A CN 201911284878 A CN201911284878 A CN 201911284878A CN 111120312 A CN111120312 A CN 111120312A
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- Prior art keywords
- screw compressor
- support structure
- gas force
- auxiliary support
- compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The application provides a design method of a screw compressor and the screw compressor. The design method of the screw compressor comprises S10, analyzing the stress of the rotor to obtain the direction of the gas force; and S20, arranging a support structure connected with the bearing seat on the shell according to the direction of the gas force, wherein the stress direction of the support structure is consistent with the direction of the gas force borne by the bearing seat. By applying the technical scheme of the invention, the bearing seat is provided with the supporting structure which is consistent with the direction of the gas force borne by the bearing seat, so that the transmission of the periodic gas force of the compressor to the outside can be reduced or blocked, the periodic fatigue damage of parts connected with the compressor can be reduced, the operation reliability of the screw compressor unit is improved, and the service life of the unit is prolonged.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a design method of a screw compressor and the screw compressor.
Background
The screw compressor is one of positive displacement compressors, and the working principle of the screw compressor is that a pair of mutually meshed and parallel arranged male and female rotors form a closed volume, the rotors are driven by a motor, the closed volume is continuously reduced along with the rotation of the rotors, gas is improved from a low-temperature low-pressure state to a high-temperature high-pressure state, and finally the process of compressing the gas is realized. During this period, the screw compressor completes the energy conversion from electrical energy to mechanical energy and then to thermal energy.
As shown in fig. 1, a motor 1 drives a male rotor 2 to rotate and cooperate with a female rotor 3 to compress gas, the volume of the gas gradually decreases from left to right, and in the process of compressing the gas by transferring energy, the screw compressor can generate gas force for exciting the vibration of compressor parts, and the gas force is transferred to the outside through bearings arranged at two ends of the rotors. As shown in fig. 2, since the suction and discharge of the screw compressor are periodic processes, the gas force of the screw compressor also exhibits periodic changes. If a weak position exists in parts in the force transmission process or the natural frequency of each order of the structure of the parts and the excitation frequency of the gas force are in the resonance range, the parts can be out of work due to the aggravation of vibration, and the compressor can not work normally. Compressor vibration has a very important impact on the performance and reliability of its operation.
Disclosure of Invention
The embodiment of the invention provides a screw compressor and a design method thereof, and aims to solve the technical problem that the screw compressor in the prior art does not well cope with vibration generated by excitation of gas force.
The embodiment of the application provides a design method of a screw compressor, and the design method comprises the following steps: s10, carrying out stress analysis on the rotor to obtain the direction of the gas force; and S20, arranging a support structure connected with the bearing seat on the shell according to the direction of the gas force, wherein the stress direction of the support structure is consistent with the direction of the gas force borne by the bearing seat.
In one embodiment, the design method further comprises: and S30, arranging a machine foot structure on the shell according to the stress direction of the supporting structure, wherein the machine foot structure is positioned in the stress direction of the supporting structure.
In one embodiment, step S30 further includes: and reinforcing ribs are arranged on the machine foot structure.
In one embodiment, the design method further comprises: and S40, carrying out harmonic response calculation on the screw compressor to obtain the vibration intensity of the machine foot structure, and designing the structure parameters of the machine foot structure and/or the reinforcing ribs according to the vibration intensity.
In one embodiment, step S10 further includes: when the rotor is subjected to stress analysis, the magnitude of gas force is also obtained; step S20 further includes: and designing structural parameters of the support structure according to the magnitude of the gas force.
The present application further provides a screw compressor, comprising: the shell is provided with a bearing seat, the screw is installed on the bearing seat, the shell is further provided with a supporting structure connected with the bearing seat, and the direction of the gas generated by the screw and borne by the bearing seat is consistent.
In one embodiment, the housing is further provided with at least one auxiliary support structure connected to the bearing seat.
In one embodiment, the auxiliary support structure comprises a transverse auxiliary support structure and an oblique auxiliary support structure, the transverse auxiliary support structure is horizontally arranged, and the oblique auxiliary support structure is obliquely arranged relative to the horizontal plane.
In one embodiment, the auxiliary support structure comprises a longitudinal auxiliary support structure, the longitudinal auxiliary support structure being arranged in a vertical direction.
In one embodiment, the bottom of the housing is further provided with a machine foot structure, and the machine foot structure is located in the stress direction of the supporting structure.
In one embodiment, the footing structure is provided with reinforcing ribs.
In one embodiment, the footing structure extends integrally at the bottom of the housing in the direction of the axis of the housing.
In the embodiment, the bearing seat is provided with the supporting structure which is consistent with the direction of the gas force borne by the bearing seat, so that the transmission of the periodic gas force of the compressor to the outside can be reduced or blocked, the periodic fatigue damage of parts connected with the compressor can be reduced, the running reliability of the screw compressor unit is improved, and the service life of the unit is prolonged.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic view of a screw compressor according to the prior art;
FIG. 2 is a schematic angular variation of rotor gas force for the screw compressor of FIG. 1;
FIG. 3 is a schematic flow diagram of a design method for a screw compressor according to the present invention;
FIG. 4 is a schematic cross-sectional view of a screw compressor according to the present invention;
FIG. 5 is a side view schematic of the screw compressor of FIG. 4;
fig. 6 is a schematic top view of the screw compressor of fig. 4.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the following embodiments and accompanying drawings. The exemplary embodiments and descriptions of the present invention are provided to explain the present invention, but not to limit the present invention.
In the working process of the compressor, the male rotor and the female rotor form a closed tooth groove, the volume of the tooth groove is continuously smaller, gas compression is achieved, meanwhile, the bearing bears gas force, and the gas force is transmitted to the outside through the bearing. The vibration (output) of the compressor structure is equal to the gas force (excitation source) multiplied by the frequency response function of the structure itself, which will cause severe vibration problems if the frequency response function has just a peak at the excitation frequency. The gas force excitation frequency of the compressor is the meshing frequency of the rotors, namely the rotating speed of the male rotor per second is multiplied by the number of teeth of the male rotor; the frequency response function of the self structure is the structural characteristic of the compressor, and the main parameter of the frequency response function is a modal parameter; for the purpose of vibration reduction, according to a model of 'source-path-receiver', it is an effective method to block the transmission path of the source and the receiver by modifying the structural characteristics of the compressor itself.
Specifically, as shown in fig. 3, in the technical solution of the present invention, the design method of the screw compressor includes S10, analyzing the force applied to the rotor to obtain the direction of the gas force; and S20, arranging a support structure 12 connected with the bearing seat 11 on the shell 10 according to the direction of the gas force, wherein the stress direction of the support structure 12 is consistent with the direction of the gas force borne by the bearing seat 11.
By applying the technical scheme of the invention, the bearing seat 11 is provided with the supporting structure 12 which is consistent with the direction of the gas force borne by the bearing seat 11, so that the transmission of the periodic gas force of the compressor to the outside can be reduced or blocked, the periodic fatigue damage of parts connected with the compressor can be reduced, the operation reliability of the screw compressor unit is improved, and the service life of the unit is prolonged.
More preferably, the design method further includes: s30, arranging the machine foot structure 14 on the shell 10 according to the stress direction of the supporting structure 12, wherein the machine foot structure 14 is located in the stress direction of the supporting structure 12, so that the machine foot structure 14 can bear gas force, further reducing or blocking the transmission of periodic gas force of the compressor to the outside, and reducing the periodic fatigue damage of parts connected with the compressor.
More preferably, in the technical solution of the present embodiment, step S30 further includes: reinforcing ribs 141 are provided on the footing structure 14. The reinforcing ribs 141 can reinforce the machine foot structure 14, and the service life of parts connected with the compressor is prolonged.
As shown in fig. 3, in the technical solution of this embodiment, the design method further includes: s40, carrying out harmonic response calculation on the screw compressor to obtain the vibration intensity of the machine foot structure 14, and designing the structure parameters of the machine foot structure 14 and/or the reinforcing ribs 141 according to the vibration intensity. It should be noted that after the vibration intensity of the machine foot structure 14 is obtained, the structural parameters of the machine foot structure 14 and/or the reinforcing bars 141 are designed to be a cooperative design associated with the whole compressor, so that the structural parameters of the machine foot structure 14 and/or the reinforcing bars 141 need to be specifically adjusted according to the actual vibration intensity feedback. Specifically, the vibration intensity of the displacement compressor can be generally evaluated to be not more than 7.1mm/s according to the measurement and evaluation of the mechanical vibration of the displacement compressor in the national standard GB-T7777-2003. Therefore, the structural characteristics of the compressor can be changed, resonance between the compressor and an excitation source is effectively avoided, and the transmission of vibration of the compressor is blocked.
More preferably, step S10 further includes: when the rotor is subjected to stress analysis, the magnitude of gas force is also obtained; step S20 further includes: the structural parameters of the support structure 12 are designed according to the magnitude of the gas forces. Therefore, the structural parameters of the supporting structure 12 can be set properly according to the magnitude of the gas force, so that the structural parameters of the supporting structure 12 meet the stress requirement, and the transmission of the periodic gas force of the compressor to the outside can be effectively reduced or blocked.
As shown in fig. 4, the present invention further provides a screw compressor, which includes a housing 10 and a screw, wherein the housing 10 is provided with a bearing seat 11, and the screw is mounted on the bearing seat 11. The shell 10 is also provided with a supporting structure 12 connected with the bearing seat 11, and the direction of the gas force generated by the screw rod born by the supporting structure 12 and the bearing seat 11 is consistent, so that the transmission of the periodic gas force of the compressor to the outside can be reduced or blocked, the periodic fatigue damage of parts connected with the compressor can be reduced, the operation reliability of the screw compressor unit is improved, and the service life of the unit is prolonged.
More preferably, as shown in fig. 4, at least one auxiliary support structure 13 connected to the bearing housing 11 is further provided on the housing 10. The auxiliary support structure 13 can perform an auxiliary support function on the bearing seat 11, so as to improve a shock absorption effect on the bearing seat 11. Optionally, in the technical solution of this embodiment, the auxiliary support structure 13 includes a transverse auxiliary support structure 131 and an oblique auxiliary support structure 132, where the transverse auxiliary support structure 131 is horizontally disposed, and the oblique auxiliary support structure 132 is obliquely disposed with respect to a horizontal plane. More preferably, the auxiliary support structure 13 further includes a longitudinal auxiliary support structure 133, and the longitudinal auxiliary support structure 133 is disposed in a vertical direction. In this way, a more comprehensive support of the bearing block 11 can be achieved.
As shown in fig. 5, the bottom of the casing 10 is further provided with a footing structure 14, and the footing structure 14 is located in the force-bearing direction of the supporting structure 12, so that the footing structure 14 can also bear the gas force, further reducing or blocking the transmission of the periodic gas force of the compressor to the outside, and reducing the periodic fatigue damage of the components connected with the compressor. More preferably, the footing structure 14 is provided with a reinforcing rib 141, and the vibration transmission of the compressor can be reduced through the reinforcing rib 141, so that the rigidity of the compressor is increased.
As shown in fig. 6, as a more preferred embodiment, the foot structure 14 integrally extends in the axial direction of the casing 10 at the bottom of the casing 10. The chassis structure 14 is thus integrated, which enhances the connection with the fixing surface. Specifically, the left end and the right end of the machine foot structure 14 are connected together, so that the number of machine foot bolts is increased, the machine foot vibration caused by individual loosening of the bolts is prevented from being increased, and the integral rigidity of the compressor can be enhanced through a plurality of constraints. Meanwhile, the machine foot structure 14 is connected with the machine body through the local reinforcing ribs 141, so that the rigidity of the compressor is further enhanced, and a better vibration reduction effect can be obtained.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes may be made to the embodiment of the present invention by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (12)
1. A method of designing a screw compressor, the method comprising:
s10, carrying out stress analysis on the rotor to obtain the direction of the gas force;
and S20, arranging a support structure (12) connected with the bearing seat (11) on the shell (10) according to the direction of the gas force, wherein the force bearing direction of the support structure (12) is consistent with the direction of the gas force borne by the bearing seat (11).
2. The design method of a screw compressor according to claim 1, further comprising:
and S30, arranging a machine foot structure (14) on the shell (10) according to the stress direction of the supporting structure (12), wherein the machine foot structure (14) is positioned in the stress direction of the supporting structure (12).
3. The design method of the screw compressor according to claim 2, further comprising in step S30: and reinforcing ribs (141) are arranged on the machine foot structure (14).
4. The design method of a screw compressor according to claim 3, further comprising:
s40, carrying out harmonic response calculation on the screw compressor to obtain the vibration intensity of the machine foot structure (14), and designing the structural parameters of the machine foot structure (14) and/or the reinforcing ribs (141) according to the vibration intensity.
5. The design method of screw compressor according to claim 1, further comprising in step S10: when the rotor is subjected to stress analysis, the magnitude of gas force is also obtained;
step S20 further includes: the structural parameters of the support structure (12) are designed according to the magnitude of the gas force.
6. A screw compressor comprising: casing (10) and screw rod, be provided with bearing frame (11) on casing (10), the screw rod is installed on bearing frame (11), its characterized in that, still be provided with bearing structure (12) that link to each other with bearing frame (11) on casing (10), bearing structure (12) with bearing frame (11) bear the direction of the gas force that the screw rod produced is unanimous.
7. -screw compressor according to claim 6, characterised in that the housing (10) is also provided with at least one auxiliary support structure (13) connected to the bearing block (11).
8. -screw compressor according to claim 7, characterised in that the auxiliary support structure (13) comprises a transverse auxiliary support structure (131) and an oblique auxiliary support structure (132), the transverse auxiliary support structure (131) being arranged horizontally and the oblique auxiliary support structure (132) being arranged obliquely with respect to the horizontal.
9. -screw compressor according to claim 8, characterised in that the auxiliary support structure (13) comprises a longitudinal auxiliary support structure (133), the longitudinal auxiliary support structure (133) being arranged in a vertical direction.
10. -screw compressor according to claim 6, characterised in that the bottom of the shell (10) is also provided with a footing structure (14), the footing structure (14) being located in the direction of the force applied by the support structure (12).
11. -screw compressor according to claim 10, characterised in that reinforcing ribs (141) are provided on the footing structure (14).
12. -screw compressor according to claim 10, characterised in that the footing structure (14) extends integrally in the axial direction of the casing (10) at the bottom of the casing (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911284878.1A CN111120312B (en) | 2019-12-13 | 2019-12-13 | Screw compressor design method and screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911284878.1A CN111120312B (en) | 2019-12-13 | 2019-12-13 | Screw compressor design method and screw compressor |
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| Publication Number | Publication Date |
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| CN111120312A true CN111120312A (en) | 2020-05-08 |
| CN111120312B CN111120312B (en) | 2023-06-20 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201911284878.1A Active CN111120312B (en) | 2019-12-13 | 2019-12-13 | Screw compressor design method and screw compressor |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4142765A (en) * | 1977-02-10 | 1979-03-06 | Sullair Corporation | Rotor bearing assembly for rotary gas machine |
| JP2006200363A (en) * | 2005-01-18 | 2006-08-03 | Fujitsu General Ltd | Hermetic compressor |
| CN102549267A (en) * | 2009-09-25 | 2012-07-04 | 东芝开利株式会社 | Hermetically sealed compressor and refrigeration cycle device employing the same |
| CN207795876U (en) * | 2017-09-20 | 2018-08-31 | 大连派思透平动力科技有限公司 | A kind of elastic shaft bearing |
| CN108561197A (en) * | 2017-12-22 | 2018-09-21 | 东方电气集团东方汽轮机有限公司 | Turbomachine Rotor support construction |
| CN109002619A (en) * | 2018-07-25 | 2018-12-14 | 四川长虹空调有限公司 | The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration |
| CN209340198U (en) * | 2018-12-25 | 2019-09-03 | 珠海格力电器股份有限公司 | Bearing support assemblies and centrifugal compressor |
-
2019
- 2019-12-13 CN CN201911284878.1A patent/CN111120312B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4142765A (en) * | 1977-02-10 | 1979-03-06 | Sullair Corporation | Rotor bearing assembly for rotary gas machine |
| JP2006200363A (en) * | 2005-01-18 | 2006-08-03 | Fujitsu General Ltd | Hermetic compressor |
| CN102549267A (en) * | 2009-09-25 | 2012-07-04 | 东芝开利株式会社 | Hermetically sealed compressor and refrigeration cycle device employing the same |
| CN207795876U (en) * | 2017-09-20 | 2018-08-31 | 大连派思透平动力科技有限公司 | A kind of elastic shaft bearing |
| CN108561197A (en) * | 2017-12-22 | 2018-09-21 | 东方电气集团东方汽轮机有限公司 | Turbomachine Rotor support construction |
| CN109002619A (en) * | 2018-07-25 | 2018-12-14 | 四川长虹空调有限公司 | The simulation optimization method of air-conditioner with fixed frequency compressor piping vibration |
| CN209340198U (en) * | 2018-12-25 | 2019-09-03 | 珠海格力电器股份有限公司 | Bearing support assemblies and centrifugal compressor |
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| Publication number | Publication date |
|---|---|
| CN111120312B (en) | 2023-06-20 |
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