CN106704179B - A kind of direct-connected double-screw compressor - Google Patents
A kind of direct-connected double-screw compressor Download PDFInfo
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- CN106704179B CN106704179B CN201710137901.9A CN201710137901A CN106704179B CN 106704179 B CN106704179 B CN 106704179B CN 201710137901 A CN201710137901 A CN 201710137901A CN 106704179 B CN106704179 B CN 106704179B
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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
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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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
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
-
- 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
- F04C2240/00—Components
- F04C2240/10—Stators
-
- 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
- F04C2240/00—Components
- F04C2240/20—Rotors
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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 present invention relates to a kind of direct-connected double-screw compressor, including casing, female rotor and male rotor, the female rotor and male rotor both ends are arranged rotor bearing respectively；The casing and female rotor, male rotor shape match and mating open up initial charge mouth and finished product gas outlet, the male rotor is equipped with rotary orientation different spiral profile sections in the same direction along its length, and the spiral profile of the female rotor is matched and engaged with male rotor；The casing corresponds to different spiral profile sections and opens up between grade gas outlet between air inlet and grade；It further include cooler, gas outlet is connected to the input port of the cooler between the grade, and the delivery outlet of the cooler is connected to air inlet between grade.The beneficial effects of the invention are as follows the effects that two-stage compressor can be realized with the scheme of similar single-stage compressor, promote compression efficiency, reduce equipment and fabricate cost.
Description
Technical field
The present invention relates to air compressor technical field, specifically a kind of direct-connected double-screw compressor.
Background technique
Compressor is a kind of driven fluid machinery that low-pressure gas is promoted to high pressure, can be divided into piston compressor,
Helical-lobe compressor, centrifugal compressor etc. are widely used in multiple technologies such as air conditioner refrigerating, pneumatic tools, rock drill, aircushion vehicle
Field.
In the running, air enters air compressor machine through air cleaner and intake valve to screw compressor in the prior art
Head, inside can generate a large amount of heat of compression when pneumatics head compresses, and oil spout is needed to be lubricated and cool down；It is compressed through pneumatics head
High temperature and pressure gas mixture is generated afterwards；Mixture enters gs-oil separator and carries out Oil-gas Separation, separates the high temperature and pressure of generation
Compressed air reaches air using moisture trap after oily fine separator and minimum pressure valve enter aerial cooler cooling
Outlet, the high temperature high pressure oil for separating generation are another with temperature control valve regulation generation after temperature control valve regulation enters oil cooler cooling
Converge all the way without cooling hot oil and enter compressor after the filtering of oily fine separator again, completes oil circulation.
The compression screw host of the prior art mostly uses structure of the level-one host in conjunction with second level host, is broadly divided into one
Three positions such as grade host, second level host and gear-box.Wherein level-one host be include two rotary shafts of yin-yang rotor and correspondence
Bearing assembly, second level host are equally independent two rotary shafts and bearing assembly, gear-box include a gear shaft and
Corresponding shaft bearing, driving master gear, two driven pinions.Usually require 5 rotary shafts, 3 gears, totally 10 portions
Position need to be positioned with bearing, and manufacturing process is complicated, and production difficulty is big.And high-speed rotating gear pair, increase the noise of complete machine.Cause
This, there are also considerable room for improvement in structure, manufacturing process and noise improvement for the two stages of compression screw host of the prior art.
The two stages of compression screw host of the prior art, since rotor tooth top seal line speed and exhaust area of eating dishes without rice or wine are smaller,
Insulation and volumetric efficiency are all lossy.In addition gear train and bearing assembly has frictional dissipation, therefore the two of the prior art
Grade compression screw host also has larger improvement space in terms of energy conservation.
Those of skill in the art improve trial to the pressure texture of single stage type, as application publication number is
A kind of " double-screw compressor for high-pressure system " of CN1793654A, " the double suction balanced type twin-screw of CN105805002A
Compressor ", " balanced double screw compressor " of CN201358919Y, CN1149108A's " is pumped particularly suitable for underwater operation
The Quimby pump of two phase fluid ", " Dual-screw rod hot oil pump " of CN2079228U, " Double-flow Quimby pump " of CN2584877Y,
" Quimby pump " of CN2578563Y is all once attempted to carry out compression efficiency promotion using the screw rod of through type, but these schemes are all
It is by rotor connecting and makes its hand of spiral be arranged to reversely improve the force environment of rotor, to increase compression efficiency
And service life.But it is confined under the conventional thinking for the protection of rotor stress, it is difficult to excavate in rotor tandem scheme
A possibility that carrying out two-stage compression, to limit the further upward mobility of compression efficiency in similar scheme.
Summary of the invention
It is an object of the invention to overcome the deficiencies in the prior art, and solving existing two-stage compressor, structure is complicated and manufacture work
Skill is complicated, and the problem of single-stage compressor inefficiency.
To achieve the above object of the invention, a kind of direct-connected double-screw compressor, including casing, female rotor and male rotor are provided,
The female rotor and male rotor both ends are arranged rotor bearing respectively；The shape of the casing and female rotor, male rotor matches simultaneously
Mating to open up initial charge mouth and finished product gas outlet, the male rotor is equipped with rotary orientation different spirals in the same direction along its length
The spiral profile of profile section, the female rotor is matched and is engaged with male rotor；The casing corresponds to different spirals
Profile section opens up between grade gas outlet between air inlet and grade；It further include cooler, gas outlet is connected to described between the grade
The input port of cooler, the delivery outlet of the cooler are connected to air inlet between grade.
Different spiral profile sections are to indicate that two sections are mutually indepedent in compression work, do not share it is identical into
Port and gas outlet, profile, the design of pitch circle helical angle can be by being designed to identical simplify industrial design process.
Preferably, correspond to that spiral profile section opens up cooling and lubricating oil-in and the thin oil return of oil enters on the casing
Mouthful；To oily fine separator is also in series between grade between air inlet, what is be arranged on oily fine separator returns the delivery outlet of the cooler
Oil pipe is connected to the thin oil return inlet of oil.
Preferably, the male rotor vacates no helical segments, the female rotor between different spiral profile sections
Corresponding male rotor is equally arranged without helical segments without helical segments position；It is empty that partition casing internal is further fixed on the casing
Between and separate the partition of compression space, the through-hole passed through without helical segments for female rotor and male rotor is opened up on the partition.
The separation of the compression space refers to that partition will be opened mutually independent two segment segregations in compression work.
Preferably, the partition opens up air inlet guide groove on one side, the air inlet guide groove from through-hole neighbouring position arrange to every
Edges of boards edge and air inlet is connected between the grade of locating spiral profile section, the air inlet guide groove are arranged in through-hole line work
For the air inlet side of division；The another side of the partition opens up outlet guide groove, and the outlet guide groove is arranged from through-hole neighbouring position
Gas outlet is connected to separator edge and between the grade of locating spiral profile section, and the outlet guide groove is arranged in be connected with through-hole
Line is as the outlet side divided.
Air inlet side is with gas side out substantially using through-hole line as division.This is because the female rotor and sun of double-screw compressor
When rotor is engaged and run, gradually expand using through-hole line as the air inlet side between cog element volume divided as rotor rotates
Greatly, gas enters between cog element volume by air inlet.After rotor rotates by a certain angle, between cog element volume crosses air inlet
Position and air inlet disconnect, and air inlet terminates.Compression stage, the between cog element volume of the between cog element volume female rotor of male rotor
It promotes in isolation each other.Rotor continues to revolve through a certain angle, i.e., rotation close to through-hole link position when, the double wedge of male rotor and
The tooth socket of female rotor constitutes a pair of new element volume again, and with the gear motion of two rotors, element volume is gradually reduced, and realizes
The compression process of gas.Compression process persistently carries out after rotor is rotated and reached using through-hole line as the outlet side divided,
Until the moment that element volume is connected with gas outlet, outlet starts compression process this moment.
Preferably, the partition disconnected along through-hole line be divided into upper board corresponding with air inlet side and with outlet side
Corresponding lower panel, the upper board and lower panel are fixed by the sealing of mutual inlay card；The air inlet guide groove and outlet guide groove point
The recessed portion that is not arranged by casing inner wall, baffle surface, baffle surface are located at what through-hole line edge and through-hole edge were arranged
Protrusion is surrounded.
Preferably, the divider upright is in female rotor and male rotor.
Preferably, the partition and female rotor is without the gap between helical segments without helical segments, male rotor
0.2mm。
Preferably, between the partition and female rotor spiral profile section, male rotor spiral profile section
Gap is 0.1mm.
Gap between partition and female rotor spiral profile section, male rotor spiral profile section is referred to
Minimum clearance distance.
Preferably, the casing corresponds to different spiral profile sections and is split as different housings section, between each shell section
It is sealed and is fixed by mutual inlay card.
In compression process, the adiabatic efficiency and volumetric efficiency of compressor determine the height of efficiency of screw rod compressor.It is more
The multi-stage compression and cascade EDFA that a spiral profile cooperation cooler in the same direction is formed, substantially increase the insulation of compressor
Efficiency；So that volumetric efficiency is got a promotion, therefore the efficiency of compressor can be improved.Cascade EDFA reduces high temperature to the shadow of rotor
Ring so that using multistage spiral profile in the same direction and elongated rotor remains unchanged the temperature ladder being able to maintain in the longitudinal direction
Degree is stablized.
Cooling and lubricating oil-in spray cooling lubricating oil reduces compression and rotation generates to carry out cooling and lubricating to rotor
Heat, reduce friction；Cooler delivery outlet contacts oily fine separator so that cutting oil and oil cooling and precipitate
The cutting oil confluence separated out is segmented, and oily thin oil return inlet injection is entered by oil return pipe, forms cutting oil circulation,
Promote cutting oil utilization efficiency.
Due to having certain pressure difference between the gas between the gas between grade near air inlet and grade near gas outlet, such as
Fruit confluence can to a certain extent influence product compressed gas quality, to lubricating oil recycle and cascade EDFA liquid can generate
It influences.And the setting without helical segments and partition can then reduce the leakage rate between this high-low pressure, so that product compresses
The stay in grade of gas.
The setting of air inlet guide groove and outlet guide groove is only arranged at spiral face type relative to conventional air inlet, gas outlet
The case where line relative position, the front/rear end of rotor helical-screw profile section can be made full use of, to include big air inlet, outlet face
Product, raising efficiency.
Partition is disconnected along through-hole line, so that partition can be close by mutual inlay card on respect to no helical segments position
Sealing is fixed, the operation being easily installed, and processing cost rises caused by avoiding the disconnection or integrated setting of rotor.Air inlet is led
Recessed portion that slot and outlet guide groove are arranged by casing inner wall, baffle surface respectively, baffle surface be located at through-hole line edge and
The protrusion of through-hole edge setting is surrounded, so that effective guide space of air inlet guide groove and outlet guide groove is maximum, to include big
Air inlet, outlet area, raising efficiency.
Divider upright is in female rotor and male rotor, so that partition is not easy to interference with rotor, while making air inlet between grade
Outlet not will receive the obstruction of partition and reduce flow velocity between grade.
Partition and female rotor without the gap between helical segments are 0.2mm without helical segments, male rotor, allow partition not
The load of yin-yang rotor is born, so that guaranteeing there are enough rotary gaps while sealing between partition and rotor, prevents from touching
Hit the loss of generation.Gap width be set as 0.2mm be because by gap width setting in this case when, can more preferably implementation
Effect is easy to cause to collide because of mismachining tolerance under existing traditional machining processes if continuing to zoom out；And if expand, can converge
Flow through it is more it is not at the same level between gas, cause product gas quality unstable.
Gap width between the partition and female rotor spiral profile section, male rotor spiral profile section is set
The reasons why being set to 0.1mm and partition and female rotor without the gap between helical segments are 0.2mm without helical segments, male rotor
The reasons why it is similar, further can also for the recessed portion of partition formed space be provided.
Casing corresponds to different spiral profile sections and is split as different housings section, passes through mutual inlay card between each shell section
Sealing is fixed.The operation being easily installed, processing cost rises caused by avoiding the disconnection or integrated setting of rotor.
The beneficial effects of the invention are as follows the effects that two-stage compressor can be realized with the scheme of similar single-stage compressor, promote pressure
Contracting efficiency reduces equipment and fabricates cost.
Detailed description of the invention
Fig. 1 is direct-connected double-screw compressor overlooking structure diagram of the invention；
Fig. 2 is direct-connected double-screw compressor positive structure diagram of the invention；
Wherein:
Air inlet between 111- grades of initial charge mouth of 1- casing 11-
Gas outlet 13- cooling and lubricating oil-in between gas outlet 121- grades of 12- finished product
The thin oil return inlet 15- level-one host shell 16- second level host shell of 14- oil
2- female rotor 3- male rotor 4- rotor bearing
5- partition 51- through-hole 54- upper board
55- lower panel 6- gland seal assembly 7- is vented side shaft holder
8- exhaust end cover
Specific embodiment
Below in conjunction with the drawings and specific embodiments, the present invention will be further described.
According to Fig. 1 to a kind of direct-connected double-screw compressor shown in Fig. 2, including casing 1, female rotor 2 and male rotor 3, institute
It states female rotor 2 and 3 both ends of male rotor is arranged rotor bearing 4 respectively；The shape phase of the casing 1 and female rotor 2, male rotor 3
Match and it is mating open up initial charge mouth 11 and finished product gas outlet 12, it is in the same direction that the male rotor 3 is equipped with rotary orientation along its length
Different spiral profile sections, the spiral profile of the female rotor 2 matches and engages with male rotor 3；The casing 1
Corresponding different spiral profile sections open up between grade gas outlet 121 between air inlet 111 and grade；Further include cooler (in figure not
Show, but those skilled in the art can be according to description understanding scheme), gas outlet 121 is connected to the cooler between the grade
Input port, the delivery outlet of the cooler is connected to air inlet 111 between grade.
Spiral profile section is corresponded on the casing 1 opens up cooling and lubricating oil-in 13 and the thin oil return inlet 14 of oil；
The delivery outlet of the cooler (is not shown in the figure, but this field skill to oily fine separator is also in series between grade between air inlet 111
Art personnel can be according to description understanding scheme), the oil return pipe being arranged on oily fine separator is connected to the thin oil return inlet 14 of the oil.
The male rotor 3 vacates no helical segments, the corresponding sun of the female rotor 2 between different spiral profile sections
Rotor 3 is equally arranged without helical segments without helical segments position；Partition 1 inner space of casing is further fixed on the casing 1
And separate the partition 5 of compression space, the through-hole passed through without helical segments for female rotor 2 and male rotor 3 is opened up on the partition 5
51。
The partition 5 opens up air inlet guide groove on one side, and the air inlet guide groove is arranged from 51 neighbouring position of through-hole to 5 side of partition
Edge and air inlet 111 is connected between the grade of locating spiral profile section, the air inlet guide groove is arranged in 51 line of through-hole
Air inlet side as division；The another side of the partition 5 opens up outlet guide groove, and the outlet guide groove is from 51 neighbouring position of through-hole
Gas outlet 121 is connected to 5 edge of partition and between the grade of locating spiral profile section for arrangement, and the outlet guide groove is arranged in
Using 51 line of through-hole as the outlet side divided.
The partition 5 disconnected along 51 line of through-hole be divided into upper board 54 corresponding with air inlet side and with outlet side pair
The lower panel 55 answered, the upper board 54 are fixed with lower panel 55 by the sealing of mutual inlay card；The air inlet guide groove and out conductance
Slot is located at 51 line edge of through-hole and through-hole 51 by 1 inner wall of casing, the recessed portion of 5 surface of partition setting, 5 surface of partition respectively
The protrusion of edge setting is surrounded.
The partition 5 is perpendicular to female rotor 2 and male rotor 3.
The partition 5 and female rotor 2 without the gap between helical segments are 0.2mm without helical segments, male rotor 3.
Gap between 2 spiral profile section of the partition 5 and female rotor, 3 spiral profile section of male rotor
For 0.1mm.
The corresponding different spiral profile sections of the casing 1 are split as different housings section, pass through phase between each shell section
Mutual inlay card sealing is fixed.
In more detail using manufactured practice as example, with actual volumetric flow 40m3/ min, rated speed 1500rpm,
On the basis of rated discharge pressure 0.8MPa.The direct-connected double-screw compressor includes female rotor 2, male rotor 3, rotor bearing 4, axle envelope
Component 6, level-one host shell 15, partition 5, second level host shell 16, exhaust side shaft holder 7, exhaust end cover 8.Air is by level-one
The initial charge mouth 11 of host shell 15 enters level-one host discharge chambe, and cutting oil moistens through the cooling of level-one host shell 15
Lubricating oil entrance 13 enters discharge chambe, passes through level-one host shell 15 by female rotor 2 and the compressed gas mixture of male rotor 3
Grade between gas outlet 121 enter external connection level-one separate cooler；It is empty through the cooling compression of level-one separation cooler separation
Gas is by air inlet 111 between the grade of second level host shell 16, into second level host discharge chambe, compressed high-pressure oil gas mixture
Enter the second-order separation cooler of external connection by the finished product gas outlet 12 of second level host shell 16；Through the second-order separation cooler
Required compressed air is obtained after separation is cooling, passes through second level host shell through the cooling lubricating oil of the second-order separation cooler separation
The thin oil return inlet 14 of 16 oil returns to two-stage compression host and carries out cooling and lubricating.
The determination method and design cycle of design parameter are as follows:
Step 1: level-one host basic parameter is confirmed according to flow and revolving speed and helical-lobe compressor molded line parameter.
Calculating formula one:
In formula: qVLevel-one helical-lobe compressor actual flow takes 40m Ru above-mentioned3/min；
ηVLevel-one helical-lobe compressor volumetric efficiency, takes 0.925；
Torsional angle coefficient, when torsion angle t takes 300 °,Take 0.9769；
Cn1Area utilization factor takes 0.4889；
N helical-lobe compressor male rotor rated speed, 1500rpm；
λ level-one helical-lobe compressor male rotor draw ratio, takes 1.41；
D1 level-one helical-lobe compressor male rotor diameter；
Above-mentioned known parameters are substituted into calculating formula one, can be derived
Helical-lobe compressor male rotor diameter D1=349.8mm；
According to the male rotor diameter D1 combination our company molded line feature shifted onto out, D1=349.8mm is taken, while showing that yin turns
Sub- diameter D2=279.7mm, center is away from C=247.5mm, male rotor pitch radius R1=112.5mm, mother rotor pitch radius R2
=135mm.
Helical-lobe compressor male rotor helix length L1=λ D1=349.8x1.41=493.2mm；
Two: T=2 π Rcot β of calculating formula,
Have again
In formula: T radius be on the cylindrical surface of R the lead of any one helix or joint away from；
The radius of periphery where the R helix；
Angle between β helical angle, the i.e. tangent line of helix and cylinder bus；
The lead T=493.2x360/300=591.86mm of the pitch circle helix of male rotor can be obtained；
Pitch circle helixangleβ=50 ° of male rotor can be obtained；
Level-one main machine structure major parameter determines as a result, is summarized as follows:
Level-one host male rotor outer diameter outer diameter 349.8mm, helix length 493.2mm, pitch radius 112.5mm, pitch circle spiral shell
50 ° of swing angle；
Level-one host female rotor outer diameter outer diameter 279.7mm, helix length 493.2mm, pitch radius 135mm, pitch circle spiral
50 ° of angle；
Level-one host yin-yang rotor center is away from 247.5mm, and 300 ° of torsion angle.
Step 2: basic according to level-one host flow and revolving speed and helical-lobe compressor molded line parameter confirmation second level host
Parameter.
Due to 0.8MPa two-stage compressor pressure at expulsion, level-one usually sets 0.25MPa, and absolute pressure indicates 0.35MPa.a；Second level
Pressure at expulsion 0.8MPa, absolute pressure indicate 0.9MPa.a.The inlet induction amount qV of split-compressor is first confirmed accordingly2。
Calculating formula three:
ε in formulaiPressure ratio in indicating；
piIndicate internal pressure end of a period pressure；
psIndicate air-breathing end of a period pressure；
V0Indicate volume when air-breathing is completed；
ViIndicate volume when compression is completed；
εVIndicate interior volume specific ratio；
κ indicates that gas isentropic index, air value usually take 1.4；
According to calculating formula three, there is one stage of compression main exhaust mouth
Obtain εV=2.447；
qV2=qV/εV=40/2.447=16.35m3/min；
According to calculating formula one:
qV2Second level helical-lobe compressor actual flow, as above takes 16.35m3/min；
ηV2Second level helical-lobe compressor volumetric efficiency is more slightly lower than level-one, takes 0.915；
Torsional angle coefficient, when torsion angle t takes 120 °,Take 1.0；
Cn1Area utilization factor takes 0.4889 with level-one host；
N helical-lobe compressor male rotor rated speed, takes 1500rpm with level-one host；
λ2Second level grade helical-lobe compressor male rotor draw ratio；
D1 second level helical-lobe compressor male rotor diameter, with level-one host male rotor diameter 349.8mm；
Above-mentioned numerical value is brought into calculating formula one, can obtain λ2=0.57；
Obtain second level male rotor length L2=0.57x349.8=199.38mm；
Equally, according toSecond level host torsion angle t2 can be corrected, 121.3 ° are obtained after amendment.
Second level main machine structure major parameter determines as a result, is summarized as follows:
Second level host uses screw rotor end face molded line identical with level-one host；
Second level host male rotor outer diameter outer diameter 349.8mm, helix length 199.38mm, pitch radius 112.5mm, pitch circle spiral shell
50 ° of swing angle；
Second level host female rotor outer diameter outer diameter 279.7mm, helix length 199.38mm, pitch radius 135mm, pitch circle spiral
50 ° of angle；
Second level host yin-yang rotor center is away from 247.5mm, and 300 ° of torsion angle.
Step 3: according to the main structure parameters of level-one host and second level host, so that it may determine level-one host shell 15 with
The structure of the components such as second level host shell 16, exhaust bearing block 7.The level-one host and second level host of the direct-connected double-screw compressor
Between by partition 5 separate, form independent air-breathing and compression chamber.Partition 5 is mounted on level-one host machine casing 15 and second level
Between host machine casing 16, the load that bearing is not subject to yin-yang rotor is not installed；Partition 5, between the diameter of axle of yin-yang rotor there are
The gap 0.2mm guarantees there are enough rotary gaps while sealing；Partition 5 is exhaust end face for one stage of compression host, right
It is air-breathing end face in second level host, therefore wants enough thickness proof strengths, it is proposed that value is 40mm；And need enough suctions
Gas gap guarantees efficiently and operates normally that level-one exhaust clearance (adding recessed portion depth) is set as 0.1mm, second level air-breathing end face
Gap (adding recessed portion depth) is set as 0.3mm；
Step 4: according to the stress load of the main structure parameters and yin-yang rotor of level-one host and second level host point
Analysis arrangement bearing assembly.
The preferred embodiment of the present invention has been described in detail above, but the invention be not limited to it is described
Embodiment, those skilled in the art can also make various etc. on the premise of not violating the inventive spirit of the present invention
Same variation or replacement, these equivalent modifications or replacement are all included in the scope defined by the claims of the present application.
Claims (8)
1. a kind of direct-connected double-screw compressor, including casing, female rotor and male rotor, the female rotor and male rotor both ends difference
It is arranged rotor bearing；The shape of the casing and female rotor, male rotor matches and mating opens up initial charge mouth and finished product goes out
Port, which is characterized in that the male rotor is equipped with rotary orientation different spiral profile sections in the same direction, institute along its length
The spiral profile for stating female rotor is matched and is engaged with male rotor；The casing corresponds to different spiral profile sections and opens up
Gas outlet between air inlet and grade between grade；It further include cooler, gas outlet is connected to the input port of the cooler, institute between the grade
The delivery outlet for stating cooler is connected to air inlet between grade；Spiral profile section is corresponded on the casing opens up cutting oil
Entrance and the thin oil return inlet of oil；For the delivery outlet of the cooler to oily fine separator is also in series between grade between air inlet, oil is thin
The oil return pipe being arranged on separator is connected to the thin oil return inlet of oil.
2. direct-connected double-screw compressor according to claim 1, which is characterized in that the male rotor is in different spiral end faces
No helical segments are vacated between molded line section, the female rotor corresponds to equally being arranged without spiral without helical segments position for male rotor
Section；It is further fixed on partition casing internal space on the casing and separates the partition of compression space, opens up confession on the partition
The through-hole of female rotor and male rotor passed through without helical segments.
3. direct-connected double-screw compressor according to claim 2, which is characterized in that the air inlet that opens up on one side of the partition is led
Slot, the air inlet guide groove are arranged from through-hole neighbouring position to separator edge and the air inlet between the grade of locating spiral profile section
Mouth connection, the air inlet guide groove are arranged in using through-hole line as the air inlet side divided；The another side of the partition opens up out
Conductance slot, the outlet guide groove are arranged from through-hole neighbouring position to separator edge and between the grade of locating spiral profile section
Gas outlet connection, the outlet guide groove are arranged in using through-hole line as the outlet side divided.
4. direct-connected double-screw compressor according to claim 3, which is characterized in that the partition is disconnected along through-hole line
It is divided into and the corresponding upper board in air inlet side and lower panel corresponding with outlet side, the upper board and lower panel to pass through mutually
Inlay card sealing is fixed；Recessed portion, the partition table that the air inlet guide groove and outlet guide groove are arranged by casing inner wall, baffle surface respectively
Face is located at edge and the protrusion of through-hole edge setting at through-hole line and surrounds.
5. direct-connected double-screw compressor according to claim 2, which is characterized in that the divider upright is in female rotor and sun
Rotor.
6. direct-connected double-screw compressor according to claim 2, which is characterized in that the partition and female rotor without spiral
Section, male rotor without the gap between helical segments be 0.2mm.
7. direct-connected double-screw compressor according to claim 2, which is characterized in that the partition and female rotor spiral end face
Gap between molded line section, male rotor spiral profile section is 0.1mm.
8. direct-connected double-screw compressor according to claim 1, which is characterized in that the casing corresponds to different spiral end faces
Molded line section is split as different housings section, is fixed between each shell section by the sealing of mutual inlay card.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710137901.9A CN106704179B (en) | 2017-03-09 | 2017-03-09 | A kind of direct-connected double-screw compressor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710137901.9A CN106704179B (en) | 2017-03-09 | 2017-03-09 | A kind of direct-connected double-screw compressor |
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| CN106704179A CN106704179A (en) | 2017-05-24 |
| CN106704179B true CN106704179B (en) | 2019-04-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710137901.9A Active CN106704179B (en) | 2017-03-09 | 2017-03-09 | A kind of direct-connected double-screw compressor |
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Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6767948B2 (en) * | 2017-08-25 | 2020-10-14 | 株式会社神戸製鋼所 | Oil-cooled two-stage screw compressor |
| CN108167189A (en) * | 2018-03-05 | 2018-06-15 | 珠海格力电器股份有限公司 | Compressor and air conditioning unit |
| WO2020123273A1 (en) | 2018-12-10 | 2020-06-18 | Carrier Corporation | Modular compressor discharge system |
| JP7246417B2 (en) * | 2019-02-06 | 2023-03-27 | 株式会社日立産機システム | multistage screw compressor |
| JP2021060003A (en) * | 2019-10-07 | 2021-04-15 | 株式会社日立産機システム | Screw compressor |
| CN111120324A (en) * | 2019-12-30 | 2020-05-08 | 浙江思科瑞真空技术有限公司 | Screw vacuum pump with multiple suction cavities and exhaust ports |
| CN112081741A (en) * | 2020-09-17 | 2020-12-15 | 湖南机油泵股份有限公司 | Method for applying pump body and pump cover to oil pumps with different flow specifications |
| WO2022179132A1 (en) * | 2021-02-26 | 2022-09-01 | 珠海格力电器股份有限公司 | Rotor assembly, compressor and air conditioner |
| CN115479027A (en) * | 2022-10-25 | 2022-12-16 | 珠海格力电器股份有限公司 | Two-stage screw compressor and air conditioning unit |
| CN219281960U (en) * | 2023-02-27 | 2023-06-30 | 开利公司 | Screw compressor and refrigerating system with same |
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| CN103967791A (en) * | 2014-05-23 | 2014-08-06 | 英诺伟特（昆山）能源机械有限公司 | Integrated screw type medium-pressure air compressor |
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| DK98144C (en) * | 1958-02-27 | 1964-03-02 | Svenska Rotor Maskiner Ab | Multi-stage compression or expansion machine with screw rotors. |
| JPS6336086A (en) * | 1986-07-30 | 1988-02-16 | Taiko Kikai Kogyo Kk | Multi-stage screw type vacuum pump |
| CN202215477U (en) * | 2011-08-22 | 2012-05-09 | 南车资阳机车有限公司 | Large-displacement variable-frequency drive screw air compressor unit |
| CN106438364B (en) * | 2016-12-13 | 2018-05-08 | 萨震压缩机（上海）有限公司 | A kind of adjustable two-stage energy-saving air compressor of pressure ratio |
| CN206636781U (en) * | 2017-03-09 | 2017-11-14 | 上海格什特螺杆科技有限公司 | A kind of new direct-connected double-screw compressor |
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| US3209990A (en) * | 1962-01-18 | 1965-10-05 | Atlas Copco Ab | Two stage screw rotor machines |
| CN103967791A (en) * | 2014-05-23 | 2014-08-06 | 英诺伟特（昆山）能源机械有限公司 | Integrated screw type medium-pressure air compressor |
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| CN106704179A (en) | 2017-05-24 |
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Effective date of registration: 20190726 Address after: 201504 No. 1555 Tingfeng Highway, Tinglin Town, Jinshan District, Shanghai Patentee after: SHANGHAI SCREW COMPRESSOR Co.,Ltd. Address before: 201504 No. 1555 Tingfeng Highway, Tinglin Town, Jinshan District, Shanghai Patentee before: SHANGHAI GLOBE SCREW TECHNOLOGY Co.,Ltd. |
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| PE01 | Entry into force of the registration of the contract for pledge of patent right | ||
| PE01 | Entry into force of the registration of the contract for pledge of patent right |
Denomination of invention: A direct connected twin screw compressor Effective date of registration: 20230912 Granted publication date: 20190412 Pledgee: Shanghai Rural Commercial Bank Co.,Ltd. Jinshan sub branch Pledgor: SHANGHAI SCREW COMPRESSOR Co.,Ltd. Registration number: Y2023310000537 |