CN101153597A - Energy-saving single-bolt compressor - Google Patents
Energy-saving single-bolt compressor Download PDFInfo
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- CN101153597A CN101153597A CNA2007100438035A CN200710043803A CN101153597A CN 101153597 A CN101153597 A CN 101153597A CN A2007100438035 A CNA2007100438035 A CN A2007100438035A CN 200710043803 A CN200710043803 A CN 200710043803A CN 101153597 A CN101153597 A CN 101153597A
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- spiral seal
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Abstract
The invention relates to compressor types, in particular to an energy saving single screw compressor of reducing leakage, improving volume efficiency and reducing energy consumption. The invention comprises a machine shell, a gas tank, a screw and a star wheel, and is characterized in that a cylindrical sealing belt part of a high pressure end of the screw is provided with a helix sealing groove. The revolving direction of the helix sealing groove is contrary with the revolving direction of a tooth groove of the screw. When the screw rotates in high speed, a sidelong wall of the helix groove can push and drive the oil liquid (and gas) in the groove and gap by sticking to produce pump delivering action. The pump delivering direction is reverse direction of the original leakage direction. The pressing head which is produced by pump delivering can partly contra or balance the pressure difference which causes leakage.
Description
Technical field
The present invention relates to the compressor class, relate to concretely a kind ofly reduce leakage, improve volumetric efficiency, thereby can reduce the energy-saving single screw compressor of power consumption, be applicable to various single screw compressors such as power (air), refrigeration and technology.
Background technique
The structure of single screw compressor is seen Fig. 1, star-wheel 2 engagements of one six groove screw rod 1 and two 11 teeth of balanced configuration, and screw rod 1, star-wheel 2 rotate in cylinder 5, casing 3 respectively, and gas is entered in the screw rod teeth groove by air aspiration cavity 9.After the star-wheel tooth sealed this teeth groove, breathing process finished, and screw rod teeth groove, star-wheel tooth and cylinder bore wall form the enclosed space that is full of low-pressure gas.Along with screw rod continues rotation, the star-wheel tooth is along the propelling of screw rod teeth groove, and enclosed space constantly dwindles, and gas pressure constantly increases, until is communicated with vent ports 7 instantaneous till compression process finish, and begin exhaust process, thereby finish the work circulation.8 is low voltage terminal, low temperature area during screw rod work, and 4 is high voltage terminal, high-temperature zone.
Because teeth groove is even bin and two star-wheels of balanced configuration on the screw rod, thereby makes the stressed complete equilibrium of screw rod, and air displacement is doubled.Therefore single screw compressor has series of advantages: screw rod does not have bending deflection, good reliability, bearing life is long, volume is little, the running vibration is little, noise is low, is particularly suitable for the middle and high work etc. of depressing.
But at present the shortcoming of the single screw compressor of producing is: leaks morely, volumetric efficiency needs raising, and its power consumption not only is higher than piston type but also is not better than double-screw type.Compressor is one of nine big power consumption equipments, is again most widely used standard equipment, and its Research on energy saving and innovative significance are great.
The screw rod of single screw compressor and cylinder bore and star-wheel are done relative rotary motion.Screw slot and star-wheel tooth slide relative.In order to guarantee that compressor runs well, must keep necessary gap between the part of relative movement, pressurized gas can leak into low pressure area and atmospheric pressure region by these gaps, and this leakage directly has influence on the minimizing of air displacement and the increase of power consumption.Reducing leakage raising volumetric efficiency is one of energy-conservation main path.
The single screw compressor engagement is complex-shaped, and leakage is more, and main leakage is seen Fig. 2,3: the gap L 1 between screw channel helix outer round surface and the cylinder bore, L2, L3; The gap L 4 of star-wheel tooth top and screw channel bottom land; Gap L 5, the L6 of forward and backward side of star-wheel tooth and the forward and backward wall of screw channel; The gap L 7 of star-wheel tooth surface and casing division surface; The gap L 8 of screw rod high voltage terminal seal section cylindrical and cylinder bore.
It is less that result of study shows that L1 to L6 leaks, L7, and L8 two places leak more, and particularly the L8 place is topmost leakage position.The L8 place is a high voltage terminal, and pressure reduction is big before and after it, and the L8 place also is that the high-temperature zone thermal expansion amount is big.Leakage-gap can not be too little in order to prevent " embracing cylinder ".Experiment and calculate the quantity of gas leakage maximum all show by herein is one of principal element that influences single screw compressor volumetric efficiency and power consumpiton.
The scheme for sealing and the design method at single screw compressor screw rod high voltage terminal L8 place are following two kinds at present:
A kind of is that screw rod high voltage terminal L8 place is cylindrical seal structure (see figure 4).This structure is the technological scheme that the most generally adopts the earliest.Sealing band cylindrical and cylinder bore diameter have certain clearance δ and length L to form flow blockage to gas leakage, realize reducing leakage rate.
Generally: δ=(3.5～4.5) * 10
-4D; L=(0.1～0.15) D; D is a cylinder bore diameter.
Another kind is that screw rod high voltage terminal L8 place is the labyrinth seal structure (see figure 5).This structure starts from Mitsui company, is improved structure, employing more.This structure is to utilize the gap delta of outer garden of sealing strip and cylinder bore diameter and the retardance and the diffusion of maze trough to come release of pressure, thereby reduces the pressure difference that gas leakage is flowed, and reduces leakage rate.
Above-mentioned two kinds of technological schemes and design method are mainly all closely related with gap delta, but, single screw compressor carries out interior cold certain thermodynamic equilibrium of keeping by oil spout, compressor can proper functioning, thereby to spray into a certain amount of fluid in the machine, and being filled with fluid in the gap, fluid can play cooling, sealing and lubrication have also brought liquid viscosity to shear power consumption simultaneously.It is also closely related with gap delta that liquid viscosity is sheared power consumption.
The amount of leakage at L8 place
Shear power N with stickiness
1Be expressed as respectively:
Above-mentioned various in: the speed of the relative cylinder bore of U-screw rod external diameter; The density of ρ and μ-oil and viscosity; P
1And P
2Pressure (the P at-leakage way two ends
1Be barometric pressure); The width of W, L, δ-leakage way, length, gap.
By the analysis showed that if reduce δ merely, increase L,, also can cause the increase of sticky shearing power consumption therebetween though can reduce leakage, even can reduce because of gap delta, leak to reduce the gained energy-saving effect and compare with the shearing power consumption of increase and cancel each other or lose more than gain and make.Thereby from working mechanism (oil spout in cold) just having restricted gap delta can not be too little.The while practical structures also limits δ can not be too little.In fact too small as if the gap, might be because of the out of roundness of cylinder bore, the malalignment of screw rod and cylinder causes gap delta inhomogeneous, if cylinder may " be embraced " because of metal friction take place screw expansion in position, the too small then little gap of δ.Therefore for single screw compressor cold in the oil spout, existing two kinds of screw rod high voltage terminal scheme for sealing deficiencys mainly are to realize that by the gap sealing is inapplicable, and its energy-saving effect is bad.
Summary of the invention
The objective of the invention is according to above-mentioned the deficiencies in the prior art part, a kind of energy-saving single-bolt compressor is provided, this compressor is between outer garden of the counterrotating screw rod of high speed and the cylinder bore certain interval being arranged, on screw rod high voltage terminal cylindrical seal position, offer spiral chute, during the screw rod high speed rotating, the spiral chute skew wall promptly the fluid in the groove and the gap (and gas) is promoted and viscosity drives, promptly produce pump action, the pumping direction is the reverse of former leakage direction, the pressure head that pump action produces can partial offset or balance cause the pressure difference of leaking, thereby solved the problem that prior art exists.
The object of the invention realizes being finished by following technological scheme:
A kind of energy-saving single-bolt compressor comprises that casing, cylinder, screw rod and star-wheel constitute, and it is characterized in that the cylindrical seal band position of screw rod high voltage terminal has the spiral seal groove, and the Hand of spiral of spiral seal groove are opposite with the Hand of spiral of screw rod teeth groove.
Described spiral seal groove is made up of the multi-head spiral seal groove.
Described multi-head spiral seal groove, its groove width 1.5～5mm; Its slot pitch be groove width (1～3) doubly; Its groove depth be groove width (0.8～1.2) doubly.
The helixangle value of described spiral seal groove is as follows: 45 °＞β＞6 °.
The optimum value of the helixangle value of described spiral seal groove is 13 °～20 °.
Described spiral seal groove place sealing strip length be the screw rod external diameter (0.1～0.15) doubly.
Sealing strip both sides, described spiral seal groove place are provided with cylindrical " Ba Qu " or " weir district ".
Described Ba Qu or weir section length be described sealing strip length (0.08～0.12) doubly.
Described spiral seal groove shape is straight shape groove or is to roll over linear grooves or be arc-shaped slot.
Described spiral seal slot cross-section is triangle or is rectangle, circular arc, trapezoidal or Straight Line and Arc combination shape.
Advantage of the present invention is, under the prerequisite that keeps all advantages of single screw compressor, adapt to characteristics cold in the oil spout and on the basis of best clearance (it is best with the sticky shearing power consumption to leak power consumption), adopt the spiral seal technological scheme, reduce to leak, improve volumetric efficiency, realize energy-conservation.
Description of drawings
Accompanying drawing 1 is a prior art single screw compressor structural representation;
Accompanying drawing 2 is accompanying drawing 1 plan view;
Accompanying drawing 3 is the main leakage way schematic representation of prior art single screw compressor;
Accompanying drawing 4 is accompanying drawing 3 local enlarged diagrams;
Accompanying drawing 5 is a prior art screw rod high voltage terminal cylindrical seal structural representation;
Accompanying drawing 6 is for now using technology screw rod high voltage terminal labyrinth seal structure schematic representation;
Accompanying drawing 7 is screw rod high voltage terminal spiral seal structural representation of the present invention;
Accompanying drawing 8 spiral chute pump actions of the present invention are analyzed schematic representation;
Accompanying drawing 9 is spiral groove seal technical parameter schematic representation of the present invention;
Accompanying drawing 10.1 is spiral seal groove straight shape groove shape schematic representation of the present invention;
Accompanying drawing 10.2 is spiral seal groove broken line shape groove shape schematic representation of the present invention;
Accompanying drawing 10.3 is spiral seal groove broken line shape groove shape schematic representation of the present invention;
Accompanying drawing 10.4 is spiral seal groove arc-shaped slot shape schematic representation of the present invention;
Accompanying drawing 11.1 is spiral seal groove triangular cross-sectional configuration schematic representation of the present invention;
Accompanying drawing 11.2 is spiral seal groove rectangular cross section structure schematic representation of the present invention;
Accompanying drawing 11.3 is spiral seal groove of the present invention trapezoid cross section structural representation;
Accompanying drawing 11.4 is spiral seal groove circular section structural representation of the present invention;
Accompanying drawing 11.5 is spiral seal groove Straight Line and Arc combination tee section structural representation of the present invention.
Concrete enforcement is vertical
Feature of the present invention and other correlated characteristic are described in further detail by embodiment below in conjunction with accompanying drawing, so that technician's of the same trade understanding:
Shown in Fig. 7-11, label 1-16 represents respectively: screw rod 1, star-wheel 2, casing 3, screw rod high voltage terminal 4, cylinder 5, hole slot 6, vent ports 7, screw rod low voltage terminal 8, air aspiration cavity 9, spiral seal groove 10, high voltage terminal sealing strip 11, fluid (gas) leak direction 12, pressure (and high pressure) district 13, high voltage terminal labyrinth seal band 14, high voltage terminal spiral seal band 15, spiral chute pumping fluid (gas) direction 16; Other labels are respectively: the Hand of spiral β of screw rod outer diameter D, cylinder bore diameter d, spiral groove seal strip length L, Ba Qu or weir section length 1, spiral seal groove, the Hand of spiral β of screw rod teeth groove
0, promote fluid (gas) power F, pumping fluid (gas) power F when spiral seal groove groove width b, spiral seal groove slot pitch t, spiral seal groove deep h, spiral chute rotation
1(axially), pumping fluid (gas) power F
2(circumferencial direction), F is decomposed into F
1And F
2Gap L 1 between screw channel helix outer round surface and the cylinder bore, L2, L3; The gap L 4 of star-wheel tooth top and screw channel bottom land; Gap L 5, the L6 of forward and backward side of star-wheel tooth and the forward and backward wall of screw channel; The gap L 7 of star-wheel tooth surface and casing division surface; The gap L 8 of screw rod high voltage terminal seal section cylindrical and cylinder bore.
The energy-saving single screw compressor that present embodiment relates to, comprise screw rod 1, star-wheel 2, casing 3, cylinder 5, hole slot 6, vent ports 7, air aspiration cavity 9, wherein screw rod 1 comprises screw rod high voltage terminal 4, screw rod low voltage terminal 8, under the situation of former best clearance (clearance leakage energy consumption and sticky shearing power consumption minimum), cylindrical seal band position (L8 place) at screw rod high voltage terminal 4 has multi-head spiral seal groove 10, and the Hand of spiral β of the Hand of spiral β of spiral seal groove 10 and screw rod teeth groove
0On the contrary, in order to increase the pumping pressure head, increase leak resistance, select β=13 °～20 °.
Spiral groove seal strip length L=(0.1～0.15) D that constitutes by multi-head spiral groove 10; Be provided with cylindrical " Ba Qu " or " weir district " in the sealing strip both sides, Ba Qu or weir section length |=0.1L
In order to improve the pumping pressure head, increase leak resistance, spiral chute should be shallow and narrow, and present embodiment is selected spiral seal groove 10 groove width b=2～3mm; Spiral seal groove 10 slot pitch t=(1～3) b; Spiral seal groove 10 groove depth h=(0.8～1.2) b.
The shape of spiral seal groove 10 can be chosen as straight shape groove (as Figure 10 .1), also can be the folding linear grooves (as Figure 10 .2,10.3), arc-shaped slot (as Figure 10 .4) etc.The cross section of spiral seal groove 10 may be selected to be triangle (as Figure 11 .1), also can be rectangle (as Figure 11 .2), circular arc (as Figure 11 .4), trapezoidal (as Figure 11 .3) or Straight Line and Arc combination shape (as Figure 11 .5) etc.
Present embodiment determines rightly as the case may be that when concrete the use above-mentioned parameters can obtain best effect.
Present embodiment is between outer garden of the counterrotating screw rod of high speed and the cylinder bore certain interval being arranged, be filled with fluid in the gap, take all factors into consideration reduce to reveal energy-conservation with reduce under the prerequisite in gap that the sticky shearing power consumption is a synthesis energy saving, adopt spiral groove seal, realize energy-conservation thereby reduce to leak the raising volumetric efficiency.
Present embodiment in the specific implementation, owing to have spiral chute 10 on the screw rod high voltage terminal cylindrical seal position, during screw rod 1 high speed rotating, the spiral chute skew wall promptly the fluid in the groove and the gap (and gas) is promoted and viscosity drives, promptly produce pump action, the pumping direction is the reverse of former leakage direction, the pressure head that pump action produces can partial offset or balance cause the pressure difference of leaking, thereby more effectively reduce or reduce " power source " of leakage flow, stop and leak, improve volumetric efficiency, realize energy-conservation.
Because present embodiment still keeps original gap delta and seal length L, thereby still has the due flow blockage release of pressure effect of prior art scheme, and corresponding sealing effect.Present embodiment has been realized more improving more effective energy-conservation.
Claims (10)
1. an energy-saving single-bolt compressor comprises that casing, cylinder, screw rod and star-wheel constitute, and it is characterized in that the cylindrical seal band position of screw rod high voltage terminal has the spiral seal groove, and the Hand of spiral of spiral seal groove are opposite with the Hand of spiral of screw rod teeth groove.
2. a kind of energy-saving single-bolt compressor according to claim 1 is characterized in that described spiral seal groove is made up of the multi-head spiral seal groove.
3. a kind of energy-saving single-bolt compressor according to claim 2 is characterized in that described multi-head spiral seal groove, its groove width 1.5～5mm; Its slot pitch be groove width (1～3) doubly; Its groove depth be groove width (0.8～1.2) doubly.
4. a kind of energy-saving single-bolt compressor according to claim 1 and 2 is characterized in that the helixangle value of described spiral seal groove is as follows: 45 °＞β＞6 °.
5. a kind of energy-saving single-bolt compressor according to claim 4, the optimum value that it is characterized in that the helixangle value of described spiral seal groove are 13 °～20 °.
6. a kind of energy-saving single-bolt compressor according to claim 1, it is characterized in that described spiral seal groove place sealing strip length be the screw rod external diameter (0.1～0.15) doubly.
7. a kind of energy-saving single-bolt compressor according to claim 1 is characterized in that sealing strip both sides, described spiral seal groove place are provided with cylindrical " Ba Qu " or " weir district ".
8. a kind of energy-saving single-bolt compressor according to claim 7, it is characterized in that described Ba Qu or weir section length be described sealing strip length (0.08～0.12) doubly.
9. a kind of energy-saving single-bolt compressor according to claim 1 and 2 is characterized in that described spiral seal groove shape is straight shape groove or is to roll over linear grooves or be arc-shaped slot.
10. a kind of energy-saving single-bolt compressor according to claim 1 and 2 is characterized in that described spiral seal slot cross-section is triangle or is rectangle, circular arc, trapezoidal or Straight Line and Arc combination shape.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007100438035A CN101153597B (en) | 2007-07-13 | 2007-07-13 | Energy-saving single-bolt compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007100438035A CN101153597B (en) | 2007-07-13 | 2007-07-13 | Energy-saving single-bolt compressor |
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| Publication Number | Publication Date |
|---|---|
| CN101153597A true CN101153597A (en) | 2008-04-02 |
| CN101153597B CN101153597B (en) | 2010-12-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007100438035A Expired - Fee Related CN101153597B (en) | 2007-07-13 | 2007-07-13 | Energy-saving single-bolt compressor |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105927542A (en) * | 2016-06-20 | 2016-09-07 | 西安交通大学苏州研究院 | Rotor shaft seal structure for double-screw compressor |
| CN106894997A (en) * | 2017-02-28 | 2017-06-27 | 西安交通大学 | A kind of ring gear formation gases compression or expansion gear |
| CN108953150A (en) * | 2018-07-04 | 2018-12-07 | 中国石油大学(华东) | A kind of single screw compressor of high interior volume specific ratio |
| CN110199089A (en) * | 2017-01-25 | 2019-09-03 | 爱德华兹有限公司 | Pump assembly with stator splice seal |
-
2007
- 2007-07-13 CN CN2007100438035A patent/CN101153597B/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105927542A (en) * | 2016-06-20 | 2016-09-07 | 西安交通大学苏州研究院 | Rotor shaft seal structure for double-screw compressor |
| CN110199089A (en) * | 2017-01-25 | 2019-09-03 | 爱德华兹有限公司 | Pump assembly with stator splice seal |
| CN106894997A (en) * | 2017-02-28 | 2017-06-27 | 西安交通大学 | A kind of ring gear formation gases compression or expansion gear |
| CN106894997B (en) * | 2017-02-28 | 2018-08-10 | 西安交通大学 | A kind of compression of ring gear formation gases or expansion device |
| CN108953150A (en) * | 2018-07-04 | 2018-12-07 | 中国石油大学(华东) | A kind of single screw compressor of high interior volume specific ratio |
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| Publication number | Publication date |
|---|---|
| CN101153597B (en) | 2010-12-29 |
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Owner name: SHANGHAI FEIHE COMPRESSOR MANUFACTURING CO., LTD. Free format text: FORMER OWNER: SHANGHAI FEIHE INDUSTRY GROUP CO., LTD. Effective date: 20080627 |
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Effective date of registration: 20080627 Address after: Postal code 518, industrial road, Shanghai, Baoshan District: 200444 Applicant after: Shanghai Feihe Compressor Manufacturing Co., Ltd. Address before: No. 518, industrial road, City Industrial Park, Shanghai, Baoshan District: 200444 Applicant before: Shanghai Feihe Industry Group Co., Ltd. |
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Owner name: SHANGHAI FEIHE INDUSTRY GROUP CO., LTD. Free format text: FORMER OWNER: SHANGHAI FEIHE COMPRESSOR MANUFACTURING CO., LTD. Effective date: 20080919 |
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Effective date of registration: 20080919 Address after: No. 518, industrial road, City Industrial Park, Shanghai, Baoshan District: 200444 Applicant after: Shanghai Feihe Industry Group Co., Ltd. Address before: Postal code 518, industrial road, Shanghai, Baoshan District: 200444 Applicant before: Shanghai Feihe Compressor Manufacturing Co., Ltd. |
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Owner name: SHANGHAI FEIHE COMPRESSOR MANUFACTURING CO., LTD. Free format text: FORMER OWNER: SHANGHAI FEIHE INDUSTRY GROUP CO., LTD. Effective date: 20120203 |
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Effective date of registration: 20120203 Address after: 200444 Shanghai city Baoshan District City Bank Road No. 118 Patentee after: Shanghai Feihe Compressor Manufacturing Co., Ltd. Address before: 200444 No. 518 Industrial Road, Baoshan District City Industrial Park, Shanghai Patentee before: Shanghai Feihe Industry Group Co., Ltd. |
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