CN203570589U - Screw compressor - Google Patents
Screw compressor Download PDFInfo
- Publication number
- CN203570589U CN203570589U CN201320677780.4U CN201320677780U CN203570589U CN 203570589 U CN203570589 U CN 203570589U CN 201320677780 U CN201320677780 U CN 201320677780U CN 203570589 U CN203570589 U CN 203570589U
- Authority
- CN
- China
- Prior art keywords
- helical
- seal
- lobe compressor
- exhaust end
- rotor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
Images
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The utility model discloses a screw compressor comprising a cylinder body, an air inlet end seat, an air inlet end cover, an air exhausting end cover and a screw rotor pair. An air inlet end shaft seal and an air inlet end bearing are mounted on the shaft sections, located at the air inlet side, of negative and positive rotors, and first air exhausting end shaft seals near a compression chamber are mounted on the shaft sections, located at the air exhausting side, of the negative and positive rotors. The screw compressor is characterized in that second air exhausting end shaft seals are mounted on the shaft sections, located at the air exhausting side, of the negative and positive rotors, so that a first seal chamber and a second seal chamber, which are located above and below the screw rotor pair, respectively, are formed between the first air exhausting end shaft seals and between the second air exhausting end shaft seals; besides, one of the first and second seal chambers is communicated with the exhaust pipe of the screw compressor, while the other one is communicated with an air inlet pipe. The screw compressor is capable of bearing higher working pressure by balancing the radial force born by the rotors with the air pressure difference between the first and second seal chambers.
Description
Technical field
The utility model relates to helical-lobe compressor.
Background technique
Helical-lobe compressor has the advantages such as reliability is high, convenient operating maintenance, strong adaptability, at aerodynamic force, rock gas, petrochemical industry, is widely used.Because helical-lobe compressor exists larger axial force and radial force, radial force is difficult to obtain effective balance, has therefore limited its working pressure.Meanwhile, because yin, yang rotor all needs to install bearing at inlet end and exhaust end, because bearing involves great expense, this also becomes the bottleneck that helical-lobe compressor further develops in high pressure field.
Summary of the invention
Technical problem to be solved in the utility model is to provide a kind of helical-lobe compressor, and it can solve the excessive problem of radial force that helical-lobe compressor exists, and makes helical-lobe compressor be competent at higher working pressure.
Further technical problem to be solved in the utility model be to provide a kind of can active balance screw rotor to the born helical-lobe compressor that points to the axial force of inlet end from exhaust end.
Helical-lobe compressor of the present utility model, comprises cylinder block, inlet end seat, air inlet end cap, exhaust end cover and screw rotor pair; Screw rotor is to being comprised of male rotor and female rotor; At male rotor and female rotor, be positioned on the shaft part of air inlet side inlet end shaft seal and inlet end bearing are installed, at male rotor and female rotor, be positioned on the shaft part of exhaust side the first exhaust end shaft seal is all installed, the first exhaust end shaft seal is near the compression chamber of this helical-lobe compressor; Be characterized in, at male rotor and female rotor, be positioned on the shaft part of exhaust side the second exhaust end shaft seal be all installed, thus between the first exhaust end shaft seal of male rotor and female rotor and the second exhaust end shaft seal, form be positioned at screw rotor to above the first Seal cage and be positioned at screw rotor to below the second Seal cage; This first Seal cage is communicated with the outlet pipe of this helical-lobe compressor with the one in the second Seal cage, and this first Seal cage is communicated with the suction tude of this helical-lobe compressor with the another one in the second Seal cage.
Above-mentioned helical-lobe compressor, wherein, exhaust end cover comprises the sidewall that roof and the periphery by roof extend to cylinder block one side direction; At male rotor, be positioned on the shaft part of exhaust side and be arranged with Balance disc, Balance disc has towards the exterior edge face of exhaust end cover roof and the interior edge face relative with this exterior edge face; The side face of Balance disc and the side wall inner surfaces of exhaust end cover are sealed and matched, thereby form the 4th Seal cage between the 3rd Seal cage between exhaust end cover roof internal surface and Balance disc exterior edge face and the second exhaust end shaft seal and Balance disc interior edge face at male rotor; The 3rd Seal cage is communicated with the suction tude of oil free screw compressor, and the 4th Seal cage is communicated with the outlet pipe of oil free screw compressor.
Above-mentioned helical-lobe compressor, wherein, the fitting surface of Balance disc and exhaust end cover is processed into labyrinth seal.
Above-mentioned helical-lobe compressor, wherein, the shaft part that male rotor and female rotor are positioned at exhaust side includes shaft shoulder section and main paragraph; Shaft shoulder section is near the compression chamber of cylinder block, and the first exhaust end shaft seal is arranged in shaft shoulder section, and the second exhaust end shaft seal and Balance disc are installed on main paragraph.
Above-mentioned helical-lobe compressor, wherein, main paragraph is frustoconic shape, and the external diameter of this main paragraph is diminished gradually by a side of the laterally closer exhaust end cover near shaft shoulder section.
Above-mentioned helical-lobe compressor, wherein, the first exhaust end shaft seal and the second exhaust end shaft seal are labyrinth seal.
Above-mentioned helical-lobe compressor, wherein, the inlet and outlet setting type of helical-lobe compressor is upper entering and lower leaving; The first described Seal cage is communicated with the outlet pipe of this helical-lobe compressor, and the second described Seal cage is communicated with the suction tude of this helical-lobe compressor.
Above-mentioned helical-lobe compressor, wherein, the inlet and outlet setting type of helical-lobe compressor is bottom in and top out; The first described Seal cage is communicated with the suction tude of this helical-lobe compressor, and the second described Seal cage is communicated with the outlet pipe of this helical-lobe compressor.
Above-mentioned helical-lobe compressor, wherein, inlet end shaft seal is between the compression chamber of cylinder block and described inlet end bearing.
Above-mentioned helical-lobe compressor, wherein, inlet end shaft seal is labyrinth seal; Inlet end bearing is comprised of with the bearing that bears axial force the bearing of bearing radial force.
The utlity model has following advantage:
1, the utility model has been cancelled the bearing setting on the yin, yang rotor shaft that is positioned at helical-lobe compressor exhaust side, by set up exhaust end shaft seal on the yin, yang rotor shaft that is positioned at helical-lobe compressor exhaust side, thereby form respectively a high-pressure sealing chamber communicating with exhaust cavity and a low pressure seal chamber communicating with air aspiration cavity in the right above and below of screw rotor of the exhaust side of helical-lobe compressor, the gas differential pressure that utilizes high-pressure sealing chamber and low pressure seal chamber to produce carrys out the radial force that balancing rotor bears, and has reduced the radial load of the inlet end bearing of helical-lobe compressor;
2, the differential pressure action that the Seal cage of Balance disc both sides produces is on Balance disc, form a gas force that is pointed to exhaust end by inlet end, balance rotor bear from exhaust end, point to the axial force of inlet end, thereby reduced the thrust load of the inlet end bearing of helical-lobe compressor;
3, the shaft part that male rotor and female rotor are positioned at exhaust side has the shape design of frustoconic shape, increased the area that Balance disc contacts with gas, thereby make the differential pressure action that produced by the Seal cage of Balance disc both sides on Balance disc and the gas force producing is larger, more effectively balance the thrust load of inlet end bearing of helical-lobe compressor;
4, the utility model has been broken through traditional bearing setting, makes axial force, the radial force of rotor obtain the balance of gas pressure, and therefore whole compressor can bear higher working pressure; In addition, owing to having cancelled the bearing setting of exhaust end, manufacture cost is decreased;
5, the first exhaust end shaft seal and the second exhaust end shaft seal all adopt labyrinth seal, in addition, the fitting surface of exhaust end cover and Balance disc is also processed into labyrinth seal, the leakage that labyrinth seal produces is internal leakage, the possibility that does not exist medium gas to reveal to the external world, and Seal Design is simple, safe and reliable to operation, can greatly simplify the design of compressor row end.
Accompanying drawing explanation
Fig. 1 is that the utility model helical-lobe compressor one embodiment's master looks cross-sectional view.
Fig. 2 is the utility model helical-lobe compressor one embodiment's the cross-sectional view of overlooking.
Fig. 3 is the utility model helical-lobe compressor one embodiment's side-looking cross-sectional view, wherein shows screw rotor to bearing the situation of downward gas radial force.
Fig. 4 is the local enlarged diagram that the utility model helical-lobe compressor one embodiment's male rotor is positioned at the shaft part of exhaust side, wherein shows screw rotor to bearing the situation of downward gas radial force.
Fig. 5 is the local enlarged diagram that the utility model helical-lobe compressor one embodiment's male rotor is positioned at the shaft part of exhaust side, wherein shows Balance disc and bear the situation of axial gas forces.
Embodiment
Below in conjunction with accompanying drawing, embodiment of the present utility model is made and being further illustrated.At this, claimant is that the model utility design to model utility is set forth using oil free screw compressor as a specific embodiment of the present utility model, it will be understood by those skilled in the art that model utility design of the present utility model is equally applicable to fuel injection helical lobe compressor.
Refer to Fig. 1 and Fig. 2.Oil free screw compressor shown in figure comprises cylinder block 1, be arranged at the inlet end seat 2 of cylinder block air inlet side, be located on inlet end seat 2 respectively and the air inlet end cap 3 of cylinder block exhaust side and exhaust end cover 4, screw rotor to and a pair of synchromesh gear 6.In cylinder block 1, be provided with suction port 18 and relief opening 19.Screw rotor is to being comprised of male rotor 51 and female rotor 52; A pair of synchromesh gear 6 is arranged at respectively on male rotor 51 and female rotor 52.At male rotor 51 and female rotor 52, be positioned on the shaft part of air inlet side inlet end shaft seal 71 and inlet end bearing 72 are installed, wherein, inlet end shaft seal 71 is between the compression chamber 11 and inlet end bearing 72 of helical-lobe compressor, and inlet end shaft seal 71 can adopt labyrinth seal; Inlet end bearing 72 is comprised of with the bearing that bears axial force the bearing of bearing radial force.At male rotor and female rotor, be positioned on the shaft part of exhaust side the first exhaust end shaft seal 81 and the second exhaust end shaft seal 82 be all installed, thus between the first exhaust end shaft seal 81 of male rotor and female rotor and the second exhaust end shaft seal 82, form be positioned at screw rotor to above the first Seal cage 12 and be positioned at screw rotor to below the second Seal cage 13.This first Seal cage 12 is communicated with the outlet pipe of this oil free screw compressor with the one in the second Seal cage 13, and this first Seal cage 12 is communicated with the suction tude of this oil free screw compressor with the another one in the second Seal cage 13.The first exhaust end shaft seal 81 can all adopt labyrinth seal near compression chamber 11, the first exhaust end shaft seals 81 and the second exhaust end shaft seal 82 of this oil free screw compressor.
In a specific embodiment, as shown in Figure 3 and Figure 4, the inlet and outlet setting type of oil free screw compressor is upper entering and lower leaving, now, because screw rotor is to bearing radial force upwards, for this radial force upwards of balance, the first Seal cage 12 is communicated with the outlet pipe of oil free screw compressor, the second Seal cage 13 is communicated with the suction tude of this oil free screw compressor.For realizing, be communicated with, can on the cylinder block sidewall on the cylinder block sidewall with respect to the first Seal cage 12 and with respect to the second Seal cage 13, offer air inlet through hole.The gas radial force that the first Seal cage 12 of cylinder block 1 and the second Seal cage 13 act on the pressure reduction formation on screw rotor can be expressed as:
F
r=(P
d-P
s)A
1
Wherein: P
dit is the gas pressure in the first Seal cage 12; P
sbe the gas pressure in the second Seal cage 13, A
1be that gas in gas and the second Seal cage in the first Seal cage acts on screw rotor to upper area.
In this embodiment, the first Seal cage 12 being communicated with the outlet pipe of oil free screw compressor becomes high-pressure sealing chamber, and the second Seal cage 13 being communicated with the suction tude of oil free screw compressor becomes low pressure seal chamber, the first Seal cage 12 and the second Seal cage 13 rely on and act on the right downward gas force of pressure reduction formation of screw rotor, balance the rotor upwards radial force of bearing, thereby reduced the radial load of inlet end bearing.
Cavity above cavity and the female rotor 52 above the male rotor 51 shown in Fig. 3 is interconnected, and the two is all a part for the first Seal cage.Similarly, the cavity of male rotor 51 belows shown in Fig. 3 and the cavity of female rotor 52 belows are also interconnected, and the two is all a part for the second Seal cage.
In another specific embodiment, the inlet and outlet setting type of oil free screw compressor is bottom in and top out, now, because screw rotor is to bearing downward radial force, for this downward radial force of balance, the first Seal cage 12 is communicated with the suction tude of this oil free screw compressor, and the second Seal cage 13 is communicated with the outlet pipe of oil free screw compressor.Like this, the first Seal cage 12 becomes low pressure seal chamber, and the second Seal cage 13 becomes high-pressure sealing chamber, the first Seal cage 12 and the second Seal cage 13 dependence act on the right pressure reduction of screw rotor and form a gas force upwards, balance the rotor downward radial force of bearing, thereby reduced the radial load of inlet end bearing.
Refer to Fig. 5.Exhaust end cover 4 comprises the sidewall 42 that roof 41 and the periphery by roof 41 extend to cylinder block one side direction.Because the rotating speed of female rotor 52 is low, the axial force of bearing is more much smaller than male rotor 51, therefore, in preferred implementation of the present utility model, at male rotor 51, be positioned on the shaft part of exhaust side and be arranged with Balance disc 10, Balance disc 10 has towards the exterior edge face 101 of exhaust end cover roof and the interior edge face 102 relative with this exterior edge face.The internal surface of the side face of Balance disc 10 and the sidewall of exhaust end cover 42 is sealed and matched, thereby forms the 4th Seal cage 16 between the 3rd Seal cage 15 between internal surface and the Balance disc exterior edge face 101 of exhaust end cover roof 41 and the second exhaust end shaft seal 82 and Balance disc interior edge face 102 at male rotor.The 3rd Seal cage 15 is communicated with the suction tude of oil free screw compressor, and the 4th Seal cage 16 is communicated with the outlet pipe of oil free screw compressor.For realizing, be communicated with, can on the exhaust end cover roof 41 with respect to the 3rd Seal cage 15 and on the cylinder block sidewall 42 relative with the 4th Seal cage 16, offer air inlet through hole.Like this, the 3rd Seal cage 15 becomes Balance disc low pressure seal chamber, and the 4th Seal cage 16 becomes Balance disc high-pressure sealing chamber, and the gas force of the differential pressure action that the 4th Seal cage 16 and the 3rd Seal cage 15 produce on Balance disc 10 can be expressed as:
F
a=P
dA
2-P
sA
3
Wherein: P
dit is the gas pressure in the 4th Seal cage 16; P
sit is the gas pressure in the 3rd Seal cage 15; A
2be that the interior gas of the 4th Seal cage 16 acts on the area on Balance disc; A
3be that the interior gas of the 3rd Seal cage 15 acts on the area on Balance disc.
The differential pressure action that the Seal cage of Balance disc both sides produces is on Balance disc 10, form a gas force that is pointed to exhaust end by inlet end, balance rotor bear from exhaust end, point to the axial force of inlet end, thereby reduced the thrust load of the inlet end bearing of helical-lobe compressor.
One preferred embodiment in, Balance disc 10 is processed into labyrinth seal with the fitting surface of exhaust end cover 4.The shaft part that male rotor 51 and female rotor 52 are positioned at exhaust side includes shaft shoulder section 501 and main paragraph 502.Shaft shoulder section 501 is near the compression chamber of cylinder block, and the first exhaust end shaft seal 81 is arranged in shaft shoulder section 501, and the second exhaust end shaft seal 82 is arranged on main paragraph 502.Main paragraph 502 is frustoconic shape, and the external diameter of this main paragraph 502 is diminished gradually by a side of the laterally closer exhaust end cover near shaft shoulder section.Balance disc 10 adopts spiral to connect with main paragraph 502, and adopts nut fastening in the exterior edge face of Balance disc 10.The screw thread rotation opposite direction of Balance disc 10 and main paragraph 502, makes being connected along with the rotation of male rotor is more and more tighter of Balance disc and male rotor.
Claims (10)
1. a helical-lobe compressor, comprises cylinder block, inlet end seat, air inlet end cap, exhaust end cover and screw rotor pair; Described screw rotor is to being comprised of male rotor and female rotor; At male rotor and female rotor, be positioned on the shaft part of air inlet side inlet end shaft seal and inlet end bearing are installed, at male rotor and female rotor, be positioned on the shaft part of exhaust side the first exhaust end shaft seal is all installed, the first described exhaust end shaft seal is near the compression chamber of this helical-lobe compressor;
It is characterized in that, at male rotor and female rotor, be positioned on the shaft part of exhaust side the second exhaust end shaft seal be all installed, thus between the first exhaust end shaft seal of male rotor and female rotor and the second exhaust end shaft seal, form be positioned at screw rotor to above the first Seal cage and be positioned at screw rotor to below the second Seal cage;
This first Seal cage is communicated with the outlet pipe of this helical-lobe compressor with the one in the second Seal cage, and this first Seal cage is communicated with the suction tude of this helical-lobe compressor with the another one in the second Seal cage.
2. helical-lobe compressor according to claim 1, is characterized in that, described exhaust end cover comprises the sidewall that roof and the periphery by described roof extend to cylinder block one side direction;
At male rotor, be positioned on the shaft part of exhaust side and be arranged with Balance disc, described Balance disc has towards the exterior edge face of exhaust end cover roof and the interior edge face relative with this exterior edge face; The side face of described Balance disc and the side wall inner surfaces of exhaust end cover are sealed and matched, thereby form the 4th Seal cage between the 3rd Seal cage between exhaust end cover roof internal surface and Balance disc exterior edge face and the second exhaust end shaft seal and Balance disc interior edge face at male rotor;
The 3rd described Seal cage is communicated with the suction tude of helical-lobe compressor, and the 4th described Seal cage is communicated with the outlet pipe of helical-lobe compressor.
3. helical-lobe compressor according to claim 2, is characterized in that, the fitting surface of described Balance disc and exhaust end cover is processed into labyrinth seal.
4. helical-lobe compressor according to claim 3, is characterized in that, the shaft part that male rotor and female rotor are positioned at exhaust side includes shaft shoulder section and main paragraph; Described shaft shoulder section is near the compression chamber of cylinder block, and the first described exhaust end shaft seal is arranged in described shaft shoulder section, and the second described exhaust end shaft seal and described Balance disc are installed on described main paragraph.
5. helical-lobe compressor according to claim 4, is characterized in that, described main paragraph is frustoconic shape, and the external diameter of this main paragraph is diminished gradually by a side of the laterally closer exhaust end cover near shaft shoulder section.
6. helical-lobe compressor according to claim 1 or 5, is characterized in that, described the first exhaust end shaft seal and the second exhaust end shaft seal are labyrinth seal.
7. helical-lobe compressor according to claim 1, is characterized in that, the inlet and outlet setting type of described helical-lobe compressor is upper entering and lower leaving; The first described Seal cage is communicated with the outlet pipe of this helical-lobe compressor, and the second described Seal cage is communicated with the suction tude of this helical-lobe compressor.
8. helical-lobe compressor according to claim 1, is characterized in that, the inlet and outlet setting type of described helical-lobe compressor is bottom in and top out; The first described Seal cage is communicated with the suction tude of this helical-lobe compressor, and the second described Seal cage is communicated with the outlet pipe of this helical-lobe compressor.
9. helical-lobe compressor according to claim 1, is characterized in that, described inlet end shaft seal is between the compression chamber of this helical-lobe compressor and described inlet end bearing.
10. helical-lobe compressor according to claim 9, is characterized in that, described inlet end shaft seal is labyrinth seal; Described inlet end bearing is comprised of with the bearing that bears axial force the bearing of bearing radial force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320677780.4U CN203570589U (en) | 2013-10-30 | 2013-10-30 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320677780.4U CN203570589U (en) | 2013-10-30 | 2013-10-30 | Screw compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203570589U true CN203570589U (en) | 2014-04-30 |
Family
ID=50538322
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320677780.4U Withdrawn - After Issue CN203570589U (en) | 2013-10-30 | 2013-10-30 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203570589U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103527481A (en) * | 2013-10-30 | 2014-01-22 | 上海齐耀螺杆机械有限公司 | Screw compressor |
| CN105114323A (en) * | 2015-09-08 | 2015-12-02 | 无锡压缩机股份有限公司 | Cylinder block structure of screw compressor |
-
2013
- 2013-10-30 CN CN201320677780.4U patent/CN203570589U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103527481A (en) * | 2013-10-30 | 2014-01-22 | 上海齐耀螺杆机械有限公司 | Screw compressor |
| CN103527481B (en) * | 2013-10-30 | 2015-12-16 | 上海齐耀螺杆机械有限公司 | A kind of helical-lobe compressor |
| CN105114323A (en) * | 2015-09-08 | 2015-12-02 | 无锡压缩机股份有限公司 | Cylinder block structure of screw compressor |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103527481B (en) | A kind of helical-lobe compressor | |
| CN203570589U (en) | Screw compressor | |
| CN205064087U (en) | Roller piston for rotary engine | |
| CN204827541U (en) | Full floating bearing turbo charger rotor system | |
| CN102926995B (en) | Bi-rotor claw-type high current pump | |
| CN204828691U (en) | Air bleeding valve and hydraulic system for hydraulic system | |
| CN105485006B (en) | A kind of helical-lobe compressor | |
| CN102135099B (en) | A kind of radial exhaust structure for rotor compressor | |
| CN203784398U (en) | Pressure sustaining valve | |
| CN105485009B (en) | A kind of brake system of car electric vacuum pump | |
| CN201568301U (en) | Vortex type compressor with floating disc | |
| CN204003568U (en) | A kind of Novel down-hole high pressure water injection pump structure | |
| CN101749235A (en) | Scroll compressor with floating disc | |
| CN206816818U (en) | A kind of combined type V-type self-tightening seal ring | |
| CN202646137U (en) | Shaft-end sealing device of centrifugal type gas compression equipment | |
| CN203500005U (en) | Auto vacuum pump | |
| CN1312437A (en) | Dry vacuum pump | |
| CN207145669U (en) | The floating sealing structure of gas seperating vale | |
| CN206377058U (en) | The water pump of rotor chamber internal and external pressure balance | |
| CN205330976U (en) | Electric vacuum pump for automobile brake system | |
| CN102425673A (en) | Oil collection ring for rotation shaft | |
| CN204113758U (en) | A kind of pump shaft balanced controls of multistage acid resistant alkali centrifugal pump | |
| CN204591672U (en) | External support rotary type fluid machine | |
| CN203500006U (en) | Automobile vacuum pump | |
| CN201225281Y (en) | Sand-proof three-screw-rod pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20140430 Effective date of abandoning: 20151216 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |