CN108194363B - Screw compressor rotor and compressor with same - Google Patents
Screw compressor rotor and compressor with same Download PDFInfo
- Publication number
- CN108194363B CN108194363B CN201810123509.3A CN201810123509A CN108194363B CN 108194363 B CN108194363 B CN 108194363B CN 201810123509 A CN201810123509 A CN 201810123509A CN 108194363 B CN108194363 B CN 108194363B
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- rotor
- screw compressor
- female
- male
- tooth
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- 238000000034 method Methods 0.000 description 14
- 230000008569 process Effects 0.000 description 14
- 238000005299 abrasion Methods 0.000 description 7
- 230000002035 prolonged effect Effects 0.000 description 6
- 230000001133 acceleration Effects 0.000 description 5
- 238000007789 sealing Methods 0.000 description 5
- 238000000926 separation method Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
Classifications
-
- 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
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/084—Toothed wheels
-
- 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
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/12—Vibration
- F04C2270/125—Controlled or regulated
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/13—Noise
- F04C2270/135—Controlled or regulated
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/16—Wear
- F04C2270/165—Controlled or regulated
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a screw compressor rotor and a compressor with the same. Wherein, screw compressor rotor includes: the female rotor and the male rotor are meshed with each other, and at any moment, the contact positions of the female rotor and the male rotor are at least two. The invention effectively solves the problems that in the prior art, the rotor of the screw compressor is easy to wear and the running performance of the rotor is influenced.
Description
Technical Field
The invention relates to the technical field of screw rotors, in particular to a screw compressor rotor and a compressor with the same.
Background
The screw compressor is a positive displacement refrigerating compressor, and utilizes a pair of intermeshing female rotor and male rotor to make rotary motion in the machine body cavity, and periodically changes the volume between every pair of tooth grooves of the rotor so as to implement the actions of suction, compression and exhaust. When the compressor runs, the male rotor drives the female rotor to rotate, and the primitive volume formed by tooth grooves of the female rotor and the male rotor, meshing lines, the cylinder and the inner wall of the end cover is continuously changed. The compressor performs a suction action when the volume of the element changes from a minimum volume to a maximum volume, and the suction is ended when the volume of the element reaches the maximum. Then, the volume of the element gradually decreases from the maximum, and the compressor starts to perform the gas compression operation. When the primitive volume begins to connect to the exhaust, the compressor performs an exhaust action until the primitive volume becomes zero. The process of exhausting once is completed, and the process is repeated along with the continuous operation of the rotor, so that the compression of the gas by the screw compressor is realized.
At present, as shown in fig. 1, in the variable frequency screw compressor, the problem of collision between male and female rotors during sudden acceleration and deceleration is caused, so that the noise of the rotors is increased, and the performance is reduced. Equidistant spacing is initially employed between the male rotor 20 'and the female rotor 10'. Wherein, the clearance D1 between the male rotor 20 'and the female rotor 10' is 0.03-0.10 mm, and is designed as an equidistant clearance. In the prior art, with the gradual increase of the rotor machining precision, the compressor displacement gradually increases, and the non-equidistant gap between the male rotor 20 'and the female rotor 10' is adopted. Specifically, as shown in fig. 2, the clearance of the rotor driving portion a ' of the male rotor 20' or the female rotor 10' is 0mm, and the remaining portions are 0.03 to 0.10mm. However, during operation of the compressor, when the male rotor 20 'suddenly decelerates, the female rotor 10' does not decelerate yet due to inertia, so that the original places with the driving gap of 0mm are separated from each other, the places with the gaps of 0.03-0.10 mm are contacted and the gaps become 0mm, which is equivalent to the impact of the female rotor 10 'on the male rotor 20', so that the abrasion of the rotor is caused, the service life of the rotor is influenced, the operation performance of the rotor is reduced, and the working efficiency of the compressor is influenced.
Disclosure of Invention
The invention mainly aims to provide a screw compressor rotor and a compressor with the same, so as to solve the problems that in the prior art, the rotor of the screw compressor is easy to wear and the running performance of the rotor is influenced.
In order to achieve the above object, according to one aspect of the present invention, there is provided a screw compressor rotor comprising: the female rotor and the male rotor are meshed with each other, and at any moment, the contact positions of the female rotor and the male rotor are at least two.
Further, the projection positions of the plural contact positions in the projection plane S perpendicular to the axial direction of the female rotor or the male rotor are fixed.
Further, there are two contact positions of the female rotor and the male rotor, the female rotor has a plurality of first teeth portions arranged at intervals along the circumferential direction thereof, the male rotor has a plurality of second teeth portions arranged at intervals along the circumferential direction thereof, at any time, two adjacent first teeth portions are engaged with one second tooth portion, and the two first teeth portions have one contact position with the second tooth portion, respectively.
Further, the rotor molded lines of the first teeth are provided with a driving part A and a sealing part B, and the contact positions of the driving part A and the sealing part B of the other first tooth adjacent to the driving part A are respectively.
Further, the portion of the second tooth portion and the first tooth portion in the meshed state between the two contact positions has a gap D.
Further, the clearance D is 0.03mm or more and 0.10mm or less.
Further, the gap D gradually increases in a direction away from the contact position.
Further, the number ratio of the plurality of second teeth to the plurality of first teeth is N and satisfiesOr/>Or (b)
According to another aspect of the present invention there is provided a compressor comprising the screw compressor rotor described above.
Further, the compressor is a variable frequency compressor.
By applying the technical scheme of the invention, the screw compressor rotor comprises a female rotor and a male rotor which are meshed with each other. At any time, there are at least two points of contact between the female rotor and the male rotor. Therefore, in the running process of the screw compressor rotor, at least two female rotors and at least two male rotors are in contact, so that the female rotors or the male rotors are prevented from being separated due to sudden acceleration and deceleration, further, the female rotors and the male rotors are prevented from being impacted due to sudden separation to cause structural abrasion, the service life of the screw compressor rotor is prolonged, and the running reliability and the working performance of the screw compressor rotor are improved. Meanwhile, in the running process of the screw compressor rotor, the vibration and noise of the screw compressor rotor can be reduced, and the use experience of a user is improved.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
FIG. 1 shows a schematic diagram of a prior art structure with equidistant gaps between the female and male rotors;
FIG. 2 shows a schematic diagram of a prior art structure with non-equidistant gaps between the female and male rotors; and
Fig. 3 shows a schematic structural view of an embodiment of a rotor of a screw compressor according to the present invention.
Wherein the above figures include the following reference numerals:
10', female rotor; 20', male rotor; 10. a female rotor; 11. a first tooth portion; 20. a male rotor; 21. and a second tooth portion.
Detailed Description
It should be noted that, without conflict, the embodiments of the present application and features of the embodiments may be combined with each other. The application will be described in detail below with reference to the drawings in connection with embodiments.
It is noted that all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs unless otherwise indicated.
In the present invention, unless otherwise indicated, terms of orientation such as "upper" and "lower" are used generally with respect to the orientation shown in the drawings or to the vertical, vertical or gravitational orientation; also, for ease of understanding and description, "left, right" is generally directed to the left, right as shown in the drawings; "inner and outer" refer to inner and outer relative to the outline of the components themselves, but the above-described orientation terms are not intended to limit the present invention.
In order to solve the problems that in the prior art, a rotor of a screw compressor is easy to wear and the running performance of the rotor is influenced, the application provides a screw compressor rotor and a compressor with the same.
As shown in fig. 3, the screw compressor rotor includes a female rotor 10 and a male rotor 20 which are engaged with each other, and at any time, there are at least two contact positions of the female rotor 10 and the male rotor 20.
By applying the technical scheme of the embodiment, in the running process of the screw compressor rotor, at least two female rotors 10 and male rotors 20 are contacted, so that the female rotors 10 or the male rotors 20 are prevented from being separated due to sudden acceleration and deceleration, further structural abrasion caused by collision of the female rotors 10 and the male rotors 20 due to sudden separation is prevented, the service life of the screw compressor rotor is prolonged, and the running reliability and the working performance of the screw compressor rotor are improved. Meanwhile, in the running process of the screw compressor rotor, the vibration and noise of the screw compressor rotor can be reduced, and the use experience of a user is improved.
As shown in fig. 3, the projection positions of the plural contact positions in the projection plane S perpendicular to the axial direction of the female rotor 10 or the male rotor 20 are fixed. Specifically, in the running process of the screw compressor rotor, in the projection plane S, the projection point of the contact position of the female rotor 10 and the male rotor 20 is unchanged, so that multiple contact positions of the female rotor 10 and the male rotor 20 are ensured at any moment, and the service life, the working performance and the working efficiency of the screw compressor rotor are prevented from being influenced due to collision between the female rotor 10 and the male rotor 20.
As shown in fig. 3, there are two contact positions of the female rotor 10 and the male rotor 20, the female rotor 10 has a plurality of first teeth 11 spaced apart along the circumferential direction thereof, the male rotor 20 has a plurality of second teeth 21 spaced apart along the circumferential direction thereof, at any time, two adjacent first teeth 11 mesh with one second tooth 21, and two first teeth 11 have one contact position with the second tooth 21, respectively. Specifically, during operation of the screw compressor rotor, the female rotor 10 and the male rotor 20 always have two contact positions, i.e. one second tooth 21 is located between the two first teeth 11 and has one contact position with each of the two first teeth 11. Wherein the projection positions of the two contact positions in the projection plane S perpendicular to the axial direction of the female rotor 10 or the male rotor 20 are fixed. In this way, the arrangement ensures that any one of the second tooth parts 21 of the male rotor 20 is positioned between any two adjacent first tooth parts 11 of the female rotor 10, so that the female rotor 10 and the male rotor 20 are prevented from being separated to cause structural abrasion, the service lives of the female rotor and the male rotor are further prolonged, and the running performance and the working reliability of the screw compressor rotor are improved. Meanwhile, vibration and noise generated in the running process of the screw compressor rotor are reduced, and the use experience of a user is improved.
As shown in fig. 3, the rotor profile of each first tooth 11 has a driving portion a and a sealing portion B, and the two contact positions are the driving portion a of one first tooth 11 and the sealing portion B of the other first tooth 11 adjacent thereto, respectively. Specifically, the relative speeds at the driving portion a and the sealing portion B are zero at the pitch circles of the tooth profiles of the two first tooth portions 11 and the one second tooth portion 21, respectively. Wherein the seal B on the same first tooth 11 is located at the rear side of the drive a when the female rotor 10 rotates counterclockwise.
As shown in fig. 3, the second tooth portion 21 and the first tooth portion 11 in the engaged state have a gap D at a portion between the two contact positions. Thus, the arrangement ensures that an oil film can be formed between the first tooth part 11 and the second tooth part 21, and structural abrasion caused by rigid contact between the first tooth part 11 and the second tooth part is prevented, so that the service life of the screw compressor rotor is prolonged, and the running performance and the working reliability of the screw compressor rotor are improved.
In the present embodiment, the clearance D is machined on the molded line of the female rotor 10, and the molded line of the male rotor 20 is unchanged.
Optionally, the gap D is 0.03mm or more and 0.10mm or less. The arrangement can ensure that an oil film is formed between the first tooth part 11 and the second tooth part 21, and can avoid the untight matching caused by overlarge gaps, so that the working reliability of the screw compressor rotor is further improved, the working performance of the screw compressor rotor is improved, and the screw compressor rotor is ensured to be capable of operating efficiently.
As shown in fig. 3, the gap D gradually increases in a direction away from the contact position. Thus, the above arrangement makes the processing of the first tooth portion 11 of the female rotor 10 easier and simpler, and reduces the labor intensity of workers.
The trend of the gap D is not limited to this. Alternatively, the gap D is unchanged in a direction away from the contact position.
Alternatively, the number ratio of the plurality of second teeth 21 to the plurality of first teeth 11 is N, and satisfiesOr/>Or (b)As shown in FIG. 3,/>Wherein the male rotor 20 has five second teeth 21 and the female rotor 10 has six first teeth 11. Thus, the gear ratio ensures that the rotor molded lines of the female rotor 10 and the male rotor 20 are smoothly connected, and no sharp point exists, thereby facilitating processing and detection. Meanwhile, the gear ratio (number ratio) ensures that the screw compressor rotor has small vibration and low noise in the running process, the female rotor and the male rotor have better rigidity, and the screw compressor rotor has smaller thermal deformation and bending deformation and is particularly suitable for being used under severe working conditions.
Specifically, in the present embodiment, the meshing gap variation rule of the first tooth portion 11 and the second tooth portion 21 is: the gap D becomes 0mm again from 0mm. Thus, when the male rotor 20 is suddenly accelerated, the male rotor 20 and the female rotor 10 are not separated, and the female rotor 10 can be rapidly accelerated; the same effect can be achieved when the male rotor 20 suddenly decelerates.
Alternatively, the curve of the mating female rotor 10 and male rotor 20 includes a circular arc and an envelope. In this way, the above arrangement can facilitate a tighter fit of the female rotor 10 and the male rotor 20, and the rotor profile is smoothly connected without sharp points.
The application also provides a compressor (not shown) comprising a screw compressor rotor as described above. Optionally, the compressor is a variable frequency compressor.
In general, the constant-frequency compressor is applied to the field of constant-frequency compressors no matter the equidistant gap design or the non-equidistant gap design, the rotating speed of the constant-frequency compressor in the running process is constant and is 2940r/m generally, and the rotor cannot accelerate or decelerate suddenly in the running process, so that the inertia of the male rotor and the female rotor is the same, and only one gap of 0mm is required to be ensured on the rotor molded line. Wherein a clearance of 0mm is normally designed at the drive of the female rotor profile. However, the variable frequency compressor carries out cold energy adjustment through rotation speed change, the motor drives the male rotor 20 to rotate, the male rotor 20 drives the female rotor 10 to move, when the male rotor 20 suddenly accelerates and decelerates, the male rotor 20 and the female rotor 10 cannot be separated, the female rotor 10 can rapidly realize acceleration and deceleration movement, further structural abrasion caused by collision of the female rotor 10 and the male rotor 20 due to sudden separation is prevented, the service life of the screw compressor rotor is prolonged, and the operation reliability and the working performance of the screw compressor rotor are improved. Meanwhile, in the operation process of the variable frequency compressor, the vibration and noise of the compressor can be reduced through the arrangement, and the use experience of a user is improved.
From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:
In the running process of the screw compressor rotor, at least two female rotors and at least two male rotors are in contact, so that the female rotors or the male rotors are prevented from being separated due to sudden acceleration and deceleration, structural abrasion caused by collision due to the sudden separation of the female rotors and the male rotors is further prevented, the service life of the screw compressor rotor is prolonged, and the running reliability and the working performance of the screw compressor rotor are improved. Meanwhile, in the running process of the screw compressor rotor, the vibration and noise of the screw compressor rotor can be reduced, and the use experience of a user is improved.
It will be apparent that the embodiments described above are merely some, but not all, embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, shall fall within the scope of the present invention.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the application described herein may be implemented in sequences other than those illustrated or otherwise described herein.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (8)
1. A screw compressor rotor comprising:
A female rotor (10) and a male rotor (20) which are engaged with each other, and at any time, the female rotor (10) and the male rotor (20) have at least two contact positions; the projection positions of the contact positions in a projection plane S perpendicular to the axial direction of the female rotor (10) or the male rotor (20) are fixed; the female rotor (10) and the male rotor (20) are arranged at two contact positions, the female rotor (10) is provided with a plurality of first tooth parts (11) which are arranged at intervals along the circumferential direction of the female rotor, the male rotor (20) is provided with a plurality of second tooth parts (21) which are arranged at intervals along the circumferential direction of the male rotor, at any moment, two adjacent first tooth parts (11) are meshed with one second tooth part (21), and two first tooth parts (11) are respectively provided with one contact position with the second tooth parts (21).
2. A screw compressor rotor according to claim 1, wherein the rotor profile of each first tooth (11) has a drive a and a seal B, the contact locations being the drive a of one first tooth (11) and the seal B of the other first tooth (11) adjacent thereto, respectively.
3. Screw compressor rotor according to claim 2, characterized in that the second tooth (21) and the first tooth (11) in the engaged state have a gap D in the part between the two contact positions.
4. A screw compressor rotor according to claim 3, wherein the clearance D is 0.03mm or more and 0.10mm or less.
5. A screw compressor rotor according to claim 3, wherein the gap D increases gradually in a direction away from the contact position.
6. Screw compressor rotor according to claim 1, characterized in that the number ratio of the plurality of second teeth (21) to the plurality of first teeth (11) is N and is such thatOr/>Or/>
7. A compressor comprising the screw compressor rotor of any one of claims 1 to 6.
8. The compressor of claim 7, wherein the compressor is a variable frequency compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810123509.3A CN108194363B (en) | 2018-02-07 | 2018-02-07 | Screw compressor rotor and compressor with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810123509.3A CN108194363B (en) | 2018-02-07 | 2018-02-07 | Screw compressor rotor and compressor with same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108194363A CN108194363A (en) | 2018-06-22 |
| CN108194363B true CN108194363B (en) | 2024-05-28 |
Family
ID=62592578
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810123509.3A Active CN108194363B (en) | 2018-02-07 | 2018-02-07 | Screw compressor rotor and compressor with same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108194363B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114320911A (en) * | 2021-12-23 | 2022-04-12 | 珠海格力电器股份有限公司 | Tooth profile curve of a pair of male and female rotors, male and female rotors and screw compressor |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6257855B1 (en) * | 1998-11-19 | 2001-07-10 | Hitachi, Ltd. | Screw fluid machine |
| JP2011074807A (en) * | 2009-09-30 | 2011-04-14 | Hitachi Industrial Equipment Systems Co Ltd | Screw compressor |
| CN102352840A (en) * | 2011-09-29 | 2012-02-15 | 陕西丰赜机电科技有限公司 | Screw rotor end face profile pair and construction method thereof |
| CN102974990A (en) * | 2012-12-18 | 2013-03-20 | 中国石油集团济柴动力总厂成都压缩机厂 | Processing method for rotor profile structure of dual-screw compressor |
| CN105370575A (en) * | 2015-11-26 | 2016-03-02 | 珠海格力电器股份有限公司 | Rotor structure and compressor comprising rotor structure |
| WO2016031413A1 (en) * | 2014-08-28 | 2016-03-03 | 株式会社Ihi | Screw rotor |
| CN208010596U (en) * | 2018-02-07 | 2018-10-26 | 珠海格力电器股份有限公司 | Rotor of helical lobe compressor and compressor with it |
-
2018
- 2018-02-07 CN CN201810123509.3A patent/CN108194363B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6257855B1 (en) * | 1998-11-19 | 2001-07-10 | Hitachi, Ltd. | Screw fluid machine |
| JP2011074807A (en) * | 2009-09-30 | 2011-04-14 | Hitachi Industrial Equipment Systems Co Ltd | Screw compressor |
| CN102352840A (en) * | 2011-09-29 | 2012-02-15 | 陕西丰赜机电科技有限公司 | Screw rotor end face profile pair and construction method thereof |
| CN102974990A (en) * | 2012-12-18 | 2013-03-20 | 中国石油集团济柴动力总厂成都压缩机厂 | Processing method for rotor profile structure of dual-screw compressor |
| WO2016031413A1 (en) * | 2014-08-28 | 2016-03-03 | 株式会社Ihi | Screw rotor |
| CN105370575A (en) * | 2015-11-26 | 2016-03-02 | 珠海格力电器股份有限公司 | Rotor structure and compressor comprising rotor structure |
| CN208010596U (en) * | 2018-02-07 | 2018-10-26 | 珠海格力电器股份有限公司 | Rotor of helical lobe compressor and compressor with it |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108194363A (en) | 2018-06-22 |
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