CN1083537C - Oil cooling type screw compressor - Google Patents
Oil cooling type screw compressor Download PDFInfo
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- CN1083537C CN1083537C CN97102361A CN97102361A CN1083537C CN 1083537 C CN1083537 C CN 1083537C CN 97102361 A CN97102361 A CN 97102361A CN 97102361 A CN97102361 A CN 97102361A CN 1083537 C CN1083537 C CN 1083537C
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
An oil-cooling type screw compressor for compressing a sucked gas by the rotation of a pair of male and female screw rotors. A first oil supplying pipeline 30 to be interconnected to an oil sump 13 of a receiver tank 12 is interconnected to a second opening 4B of a cylinder 4. A second drainage recovering pipeline 36 to be interconnected to a bottom part of the oil sump 13 of the receiver tank 12 is joined together with a third oil recovering pipeline 40 to be interconnected to the bottom of an oil separator 14 and then is interconnected to a first opening 4A opened to a working space just before the discharge of the cylinder 4. The second opening 4B is installed in a position being further nearer to the inlet side than the first opening 4A.
Description
Technical field
The present invention relates to oil-cooled type screw compressor, especially do not need to extract out the oil-flooded screw compressor of the condensed water operation in the gas holder.
Background technique
Existing oil-flooded screw compressor, compress the ambient atmosphere that imports by suction passage by the rotation that is arranged at a pair of convex-concave helical rotor in the cylinder barrel, pressurized air becomes the pressurized gas of high temperature and the fluid-mixing of oil, and the exhaust port of this fluid-mixing from cylinder barrel is sent in the gas holder.Then, larger oil droplet falls to storing in the oil sump of gas holder below by proportion difference.On the other hand, the mixed gas of vaporific pressurized air and oil is separated into pressurized gas and oil by the oil separator that is arranged in the gas holder, and the pressurized air that has purified is transported to the consumption side from supplying mouth.In addition, store the oil in the oil sump of gas holder below, under the effect of the compressed-air actuated pressure in this gas holder, offer the cooling that is used in compression the space in, lubricate, sealing between helical rotor and cylinder barrel, and the bearing of supporting helical rotor axle, gland seal device etc. is lubricated.
Such oil-cooled type screw compressor is in the importing ambient atmosphere it to be compressed, supply to the consumption side after temporarily storing in gas holder, and when compressed-air actuated consumption tails off, the compressed-air actuated holdup time of gas holder is elongated, therefore, compressed-air actuated temperature also reduces during this, so, this airborne moisture dewfall in gas holder becomes condensed water and stores oil sump bottom in gas holder.And when having accumulated this condensed water, then condensed water mixes with oil phase, causes the proterties deterioration and the emulsion of oil.The problem of Cun Zaiing is thus: since therefore will be and deterioration or emulsification oil and the mixed solution of condensed water is delivered in the cylinder barrel and bearing means etc., make it produce sintering or get rusty in the inside of each machine at sliding position so can not play normal cooling, effect such as lubricated.Therefore trouble is, when begin operation every day, must open valve one by one, and the condensed water that stores in gas holder oil sump bottom is discharged.
As the structure that does not need such discharge condensed water operation, the oil-cooled type screw compressor that Japanese patent gazette is special fair 7-117051 number is well-known.The structure of this existing oil-cooled type screw compressor, it will be stored in the oil of gas holder below and the mixture of condensed water, bottom from gas holder, the condensed water that top cover portion produced with oil separator, utilize gland, import in the low rotor chamber of pressure in this gas holder of pressure ratio with direct pipeline, be discharged to the consumption side with being compressed hot warmed-up pressurized air, thereby remove the operation of above-mentioned extraction condensed water.
But, there is following problem in this existing oil-cooled type screw compressor: first, the lubricant oil that imports in the action space from the gas holder below cools off, lubricates, seals action space,, because condensed water and oil are imported into admixture, especially under the long environment of the pressurized air holdup time in few at high humidity and consumed cabin air amount, the gas holder, also produce many condensed waters, thereby the moisture ratio in the oil is big, has therefore consequently promoted the sintering and the abnormal wear that produce because of each slide part insufficient lubrication.Second, because contain the importing position of the oil of condensed water and be locations of low pressure from the suction port of compressor to the compression space range, so in above-mentioned condensed water imports later path in position and action space, be easy to generate a large amount of rust, and owing to be in the middle of the process at compression initial stage, so compressed-air actuated temperature rises so not highly.The 3rd, corresponding with the consumed cabin air amount that consumes side, open and close at control capacity regulating device, promptly between so-called full load operation and no-load running during repeatable operation, when no-load running, the capacity regulating device is a closed condition, stops to suck in cylinder barrel air.Therefore, its built in problem is, because the suction side in the compressor main body becomes negative pressure, further increases with pressure reduction in the gas holder, the influx of flow of lubricant in action space that contains condensed water also increases, so the kinetic equation loss of compressor main body further increases.
Therefore, purpose of the present invention will provide a kind of oil-flooded screw compressor exactly.It can be addressed the above problem, and each sliding position to convex-concave helical rotor, cylinder barrel etc. is lubricated well, can carry out the recovery of condensed water well simultaneously.
Summary of the invention
The oil-flooded screw compressor of a first aspect of the present invention is provided with: a pair of convex-concave helical rotor that will rotate freely is accommodated in the interior compressor main body of housing; Be arranged at capacity regulating device this compressor main body suction port, that control suction air quantity is used; Be communicated with the gas holder that is provided with the exhaust port of above-mentioned compressor main body; Be connected with this gas holder, the oil separator that will separate away from the oil the pressurized air that compressor main body is discharged, this oil-flooded screw compressor, its structure is: in the cylinder barrel of the housing of taking in above-mentioned helical rotor, suction side at potted line nearby is equipped with first opening, the sealing line potted line of the capable convex-concave helical rotor that seals in the ban is in when beginning drain position, with the suction side distance of this helical rotor groove width is only arranged, on the other hand, also be equipped with second opening, the position of second opening is than the close more suction side of first opening, and than the also close side of discharging of potted line, when the sealing line is in the position of putting the suction air into when the back capable potted line of above-mentioned convex-concave helical rotor, with discharge side the distance of this helical rotor groove width only arranged, first pipeline that fuel feeding is used is connected with this second opening.This first pipeline is connected with top position, gas holder oil sump bottom, on the other hand, second pipeline that condensed water reclaims usefulness is connected with gas holder oil sump bottom, the 3rd pipeline that oil reclaims usefulness is connected with the bottom of above-mentioned oil separator, and second pipeline is collaborated with the 3rd pipeline, is connected with first opening of above-mentioned housing then.Thereby the pure oil that only will not contain condensed water by first pipeline imports to second opening, this second opening is opened in not the action space with the air-tight state that sucks spatial communication, after the sea surface oil slick that makes convex-concave helical rotor and cylinder barrel really forms, only will store in the condensed water of oil sump bottom by second pipeline and to take out, in addition, owing to make its interflow by the 3rd pipeline, the 3rd pipeline is the pipeline that reclaims the recovered oil of trace from the bottom of oil separator, import to above-mentioned first opening then, so can make condensate evaporation by the heat of compression of the high temperature compressed gas that will discharge, outside pressurized air is discharged to gas holder at once.
The oil-flooded screw compressor of a second aspect of the present invention, owing to be arranged at above-mentioned second aperture position on the above-mentioned housing, distance first aperture position is provided with the interval greater than the helical rotor groove width, therefore, make it after positively having formed the oil film of each one in convex-concave helical rotor and the cylinder barrel in advance by the pure lubricant oil that imports from above-mentioned second opening, import condensed water by first opening, so can prevent the disadvantage of being broken and producing because of oil film along with the importing of condensed water, slide part.
The oil-flooded screw compressor of a third aspect of the present invention by being provided with throttle valve midway at above-mentioned second pipeline, importing to first opening in the condensed water of oil sump bottom and reclaims because only will store, so kinetic equation loss can be suppressed at minimum limit.
The oil-flooded screw compressor of a fourth aspect of the present invention, owing to make the internal diameter of above-mentioned second pipeline littler than the internal diameter of first pipeline, so can omit second pipeline throttle valve midway.
The oil-flooded screw compressor of a fifth aspect of the present invention, because the through oil hole at above-mentioned first pipeline that is communicated with above-mentioned oil sump is provided with the body that prevents that prevents to suck condensed water, sucks condensed water, can only the pure lubricant oil that does not contain condensed water be supplied to action space so can stop from through oil hole.
Description of drawings
Fig. 1 is the sectional drawing of expression one embodiment of the invention.
Fig. 2 is the sectional drawing of the suction oral-lateral of expression one embodiment of the invention.
Fig. 3 is the unfolded drawing of the jar tube of expression one embodiment of the invention.
Embodiment
Below see figures.1.and.2 the first embodiment of the present invention is described.As shown in Figure 1, oil-cooled type screw compressor main body 1 is taken in rotation intermeshing a pair of convex-concave helical rotor 2,2A (shown in Figure 1 only is protruding helical rotor 2) freely in the cylinder barrel 4 of housing 3.The suction passage 6 that is used to import outer gas is connected with the suction port 5 that is arranged at these cylinder barrel 4 one sides, be provided with filter by suction 7 at this suction passage 6, and, between this filter by suction 7 and suction port 5, be provided with air-breathing blocking valve 9, promptly when the pressure in the gas holder described later is higher than setting pressure, close valve interlock capacity regulating device suction passage 6, that control suction air quantity is used by regulator 8.On the other hand, the discharge stream 11 of gas holder 12 by having one-way valve 11A be arranged at figure in the exhaust port 10 of cylinder barrel 4 belows be connected.This gas holder 12 is provided with oil sump 13 in the bottom, be provided with oily separatory oil separator 14 on top, and the top of this oil separator 14 is provided with top cover portion 15, is used for and consumes the switch valve 17 that side 16 is connected and be connected with this top cover portion 15.Also have, on cylinder barrel 4, be equipped with the aftermentioned first and second opening 4A, 4B, this opening 4A, 4B are connected with first and second pipelines described later, in addition, use the other end of stream 18 by the control that an end is communicated with top cover portion 15, be connected with above-mentioned regulator 8, thereby the interior pressure of gas holder 12 is imported to regulator 8, make it can the air-breathing blocking valve 9 of open and close.
On above-mentioned a pair of convex-concave helical rotor 2,2A, be respectively equipped with the coaxial suction side shaft 19 of this helical rotor 2 and discharge side shaft 20.And, in the inboard of the bearing chamber 3A that is arranged at housing 3 one sides, be provided with the bearing 22 and the gland seal device 23 of the suction side shaft 19 that supporting rotates freely.Also have, the end that sucks side shaft 19 at protruding helical rotor 2 is provided with driven pulley 24, on the line shaft of prime mover-motor 25, be provided with drive pulley 26, between driven pulley 24 and drive pulley 26, belt 27 be installed, drive protruding helical rotor 2 rotations.Drive the recessed helical rotor 2A rotation that is meshed with protruding helical rotor 2 simultaneously.In the inboard of the bearing chamber 3B that is arranged at housing 3 opposite sides, be provided with gland seal device 28 and support the bearing 29 of discharging side shaft 20 freely rotationally.
Top position, bottom at the oil sump 13 of gas holder 12, be connected with first pipeline 30 that supplying lubricating oil that an end is connected with through oil hole 30A is used, the second opening 4B on making its other end 30B and being arranged in cylinder barrel 4 is connected, and is provided with oil cooler 31 and oil strainer 32 in the centre of this first pipeline 30.At the through oil hole 30A that is arranged at above oil sump 13 bottoms, be provided with the body that prevents that prevents to suck condensed water, it is balk board 33, suction side at oil cooler 31 is provided with the oily temperature autocontrol valve 34 that carries out switch according to oily temperature, is provided with the bypass line 35 that is set up in parallel with oil cooler 31 on this oil temperature autocontrol valve 34.Be connected with the 2nd pipeline 36 that condensed water that an end is connected with 36A reclaims usefulness in oil sump 13 bottoms of gas holder 12, its the other end 36B is connected with the above-mentioned second opening 4B on being arranged in cylinder barrel 4, is provided with oil strainer 37 and throttle valve is a throttle orifice 38 on this second road pipe 36.In the bottom of oil separator 14, be to be connected with the 3rd pipeline 40 that the separating oil that is connected with an end 40A reclaims usefulness on the oil sump 39, its the other end 40B is connected with the outlet side of the throttle orifice 38 of second pipeline 36 with coarse-grain filtering device 40D by throttle valve 40E, one-way valve 40C, oil from throttle orifice 38 collaborates with the separating oil of the trace that reclaims from above-mentioned oil separator 14, receives on the first opening 4A of cylinder barrel 4.Also have, the pipeline internal diameter of second pipeline 36 is littler than the internal diameter of first pipeline 30.In addition, with an end 41A, the 42A of first, second branch line 41,42 respectively be arranged at first pipeline 30 on the outlet side of oil strainer 32 be connected, and its other end 41B, 42B are connected with bearing chamber 3A, 3B respectively.
Below the above-mentioned first opening 4A and the second opening 4B are described.Shown in Figure 2 is the suction side end face of a pair of convex-concave helical rotor 2,2A, and the part that double dot dash line is enclosed among the figure is the suction end face 43 of housing 3.In addition, shown in Figure 3 is the unfolded drawing of cylinder barrel 4 inwalls, on behalf of upside, downside among suction port 5, the figure to represent exhaust port 10 among the figure, and a～f represents the position relation of the potted line of the inwall of cylinder barrel 4 and protruding helical rotor 2 among the figure, and g～l represents the position of the potted line of recessed helical rotor 2A.And while be meshing with each other when rotating as convex-concave helical rotor 2,2A, each potted line of convex-concave helical rotor 2,2A moves from the suction side to discharging side (top the figure) successively, dwindles its spatial volume gradually, carries out compression continuously.For ease of explanation, below protruding helical rotor 2 one sides are described, and because for recessed helical rotor 2A one side, roughly be symmetry and be the same space, so omit its detailed explanation.At first, when rotation owing to protruding helical rotor 2, in advance the potted line of sealing (to call potted line in advance in the following text) X is when the position of potted line b moves to the position of potted line c, d, e, f, and the groove width amount of the protruding helical rotor 2 of back row i.e. potted line (the to call back row potted line in the following text) x ' that seals of a pitch (P) also moves to potted line b, c, d, e from the position of a successively.Equally, when rotation owing to recessed helical rotor 2A, potted line in advance (to call potted line in advance in the following text) y is when the position of h moves to i, j, k, l, and the groove width of the recessed helical rotor 2A of back row i.e. a pitch and potted line (the to call back row potted line in the following text) y ' that seals also moves to the position of h, i, j, k successively from potted line g.Arrive position-potted line b, the h that puts the suction air at go ahead of the rest potted line x, y, simultaneously, when back row potted line x ', y ' arrival potted line a, g, suck air in the formed slot space of potted line x, y in advance with above-mentioned.In convex-concave helical rotor 2,2A rotation, potted line x, y suck air before potted line c, i and back row potted line x ', y ' arrival potted line b, the h continuously in advance.At back row potted line x ', when y ' arrives potted line b, h, when promptly going ahead of the rest potted line x, y arrival c, i, suck air and finish, simultaneously, the action space that potted line b, c, h, i and cylinder barrel 4 are surrounded begins to be compressed.Along with the continuous rotation of a pair of convex-concave helical rotor 2,2A, (x y) arrives potted line (d at the potted line of going ahead of the rest, j), (e, k), (f, l), while back row potted line (x ', y ') arrives (c, h), (d, j), (f is in the time of k), suck air and dwindle volume successively, the action space that is enclosed by potted line c, d, i, j and cylinder barrel 4, the action space that is enclosed by potted line d, e, j, k and cylinder barrel 4, the action space that is enclosed by potted line e, f, k, l and cylinder barrel 4 are compressed thereupon.When in advance potted line x, y arrive beginning drain position-potted line f, l (this moment back row potted line x ', y ' be positioned at potted line e, k), begin to discharge pressurized air from this position, and as back row potted line x ', when y ' arrives potted line f, l, discharge and finish.
And, the above-mentioned first opening 4A nearby wears in the suction side of the potted line e adjacent with the suction side, when sealing line e was positioned at beginning drain position-potted line f in advance potted line x, the y of protruding helical rotor 2, the groove width that this protruding helical rotor 2 only arranged with it in the suction side i.e. the distance of a pitch (P).On the other hand, the second opening 4B, and also will wear near the position of discharging side in this position (potted line b) of closing into the suction air more near the suction side than the first opening 4A, closes that to go into to suck air be that back capable potted line x ' by protruding helical rotor 2 closes.The position of this second opening 4B, the above interval L of the above i.e. pitch of the groove width of protruding helical rotor 2 (L＞P) preferably is set apart from the position of the first opening 4A, as for the Design of length of helical rotor must more not necessarily also can more than the pitch at one.
Below the effect of said structure is described.When motor 25 startings, protruding helical rotor 2 and recessed helical rotor 2A are meshing with each other on one side, rotation on one side, thus, ambient atmosphere flows into suction passage 6 by filter by suction 7, air-breathing blocking valve 9 by opening state arrives suction port 5, is compressed by convex-concave helical rotor 2,2A and cylinder barrel 4 formed action spaces.At this moment, do not contain the pressure difference of the pure oil 0 of condensed water D by action space and gas holder 12, direct into action space from the through oil hole 30A of oil sump 13 by first pipeline 30, this action space is cooled off, lubricates, seals, carry out the formation of oil film in this stage really.Then, pressurized air and the oil that becomes the gas-liquid mixed state in this action space is arranged to exhaust port 10.The pressurized air of the gas-liquid mixed state of this discharge and oil are pressed to gas holder 12 by discharging stream 11.Then in this gas holder 12, larger oil droplet drips by proportion difference and stores in the oil sump 13 below gas holder 12.On the other hand, the mixed gas of vaporific pressurized air and oil is separated into pressurized air and oil by oil separator 14, become pure pressurized air be sent to by top cover portion 15 and consume side 16.Also have, make it under the temperature of the oil that passes through first pipeline 30 situation lower than set point of temperature, the oil of part or all supplies to action space by oil temperature autocontrol valve 34 by bypass line 35, on the other hand, make it under the temperature of the oil situation higher, supply to action space by the oil that oil cooler 31 will cool off by oil temperature autocontrol valve 34 than set point of temperature.In addition, from the way of first pipeline 30, tell first, second branch line 41,42, make its bearing chamber 3A, 3B of accommodating bearing 22,29 and gland seal device 23,28 by 41,42 pairs of first, second branch lines supply with pure lubricant oil 0, this bearing 22,29 and gland seal device 23,28 are cooled off, lubricate, seal.
In addition, the pipeline of top cover portion 15 outlets is connected with regulator 8 with stream 18 by control, it is worked as close air-breathing blocking valve 9 when gas holder 12 interior pressure reach authorized pressure.
Even, store condensed water D in gas holder 12 oil sumps 13 bottoms from second pipeline 36, by store micro-separating oil 0 in the oil sump 39 of oil separator 14 ' three pipelines 40 such as recovery road-wait, collaborate at its other end 40B, with condensed water D, be directed to the compression space that at once will discharge (part of being enclosed by potted line d, e, j, k and cylinder barrel 4) by the first opening 4A.And, these oil 0 ' and condensed water D import by the pressure in the gas holder 12 and the pressure reduction of the first opening 4A side pressure, two pressure, pressure reduction in this action space as mentioned below and the gas holder 12 is less, and because of being positioned at from sucking action space position far away, so this action space is difficult for when no-load running by about the influence of negative pressure institute.So, with oil 0 ' admixture import to the condensed water D in the compression space that at once will discharge from the first opening 4A, the heat of compression by the high temperature compressed air that will discharge is evaporated at once, be pressed in the gas holder 12 by discharging stream 11 with pressurized air, through after the oil separator 14, be discharged to outside the gas holder 12.
As mentioned above, at present embodiment, owing to store in the condensed water D of gas holder 12 oil sumps 13 bottoms, evaporated by the heat of compression of high temperature compressed air in the compression space that horse back in compressor main body 1 will be discharged, condensed water is discharged to outside the gas holder 12 by discharge stream 11, gas holder 12, oil separator 14 with pressurized air, so can not store in oil sump 13.
In addition, with regard to the above-mentioned first opening 4A with regard to the position in the cylinder barrel 4 relation, be to wear near the suction side on potted line e, when sealing line e was positioned at the position that begins to discharge-potted line f position at the in advance potted line x of protruding helical rotor 2, having only the groove width of this protruding helical rotor 2 with the suction side was the distance of a pitch (P) of rotor.This position promptly is not connected with exhaust port 10, and from sucking action space farthest, yes and the close confined space of pressure of gas holder 12 sides, so even this action space is in the variation along with the consumed cabin air amount, compressor full load and zero load between under the situation about changing repeatedly, variation in pressure is also seldom.Therefore, the changes in flow rate of the separating oil 0 ' that imports by the condensed water D that pressure reduction imported between action space and the gas holder 12 and from oil separator 14 is also few, so do not contain as existing structure, when no-load running, import a large amount of condensed water D and oil 0 ' by the negative pressure that sucks in the action space, thereby produce significantly kinetic equation loss.In addition, be directed to the compression space that to discharge at once because of condensed water D, because the rubbish and the mud of sneaking among this condensed water D are discharged from exhaust port 10 immediately, so can prevent from thereby the gap between its engaging-in convex-concave helical rotor 2,2A and the cylinder barrel 4 is damaged the accident of compressor, and abrasion of the convex-concave helical rotor 2,2A and the cylinder barrel 4 that do not produce therefrom.In addition, because condensed water D is directed to the action space that the horse back that is under high temperature, the high pressure conditions will be discharged, so, evaporation condensed water D positively.And, because the state of condensed water D to mix mutually with the oil 0 ' of oil sump 39, import to the compression space by the 3rd pipeline 40,, can only reclaim quantitative condensed water D all the time so can not reduce the greasy property of the convex-concave helical rotor 2,2A and the cylinder barrel 4 that constitute above-mentioned action space.
In addition, because by first pipeline 30, will be from the through oil hole 30A of oil sump 13 pure oily 0, import to the compression space that potted line c, d, i, j are surrounded from the second opening 4B, so can cool off, lubricate, seal convex-concave helical rotor 2,2A and cylinder barrel 4 really.Also have, because above-mentioned oily 0 imports in the compression space of suction process after finishing, so thereby pressurized air in this oil reexpanded, reduces compressor in suction port 5 suction air quantity can not occur being contained in reduces its performance, produces this class situation of kinetic equation loss.In addition, because oil 0 is directed to the action space before condensed water D imports, so, can be pre-formed oil film on the surface of above-mentioned helical rotor 2,2A and cylinder barrel 4 in the compression space, can be lubricated well, and the sintering that can avoid the corrosion that produces because of condensed water and produce because of lack of lubrication.And, because of first, second branch line 41,42 by going out in 30 minutes from first pipeline, pure oil 0 is imported to bearing chamber 3A, 3B, thus can prevent bearing 22,29 and gland seal device 23,28 sintering, can also seal by 23,28 pairs of gases of gland seal device.
By middle district throttle valve-throttle orifice 38 is set at second pipeline 36, the condensed water D that comes from the oil sump 13 bottom force feeds of gas holder 12 is applied resistance, can limit and the corresponding discharge capacity of its generating capacity, so can only separate out condensed water D, make it evaporate efficiently, be discharged to outside the gas holder 12 in the compression space that will discharge at once by the pressurized air of high temperature.
Because the internal diameter of above-mentioned second pipeline 36 designs forr a short time than the internal diameter of first pipeline 30, so can omit above-mentioned throttle orifice 38, can reduce the flow section of the condensed water D that comes from the oil sump 13 bottom force feeds of gas holder 12, can only condensed water D be imported in the compression space that to discharge, make it at once in this action space making high-efficiency comprehensive ground evaporation.
Owing to be provided with balk board 33 at the through oil hole 30A of first pipeline 30 that is communicated with oil sump 13, import to the second opening 4B, one side and bearing chamber 3A, 3B from through oil hole 30A so can only will not sneak into the pure oil 0 of condensed water D.
The present invention is not limited to the foregoing description, can famous kind be out of shape, for example, at present embodiment, first, second opening is arranged on the cylinder barrel of protruding helical rotor side, but also can be arranged on the cylinder barrel of recessed helical rotor side, in addition, except that the stage compressor as present embodiment, the senior side of multistage compressor also can adopt same structure.
The oil-flooded screw compressor of a first aspect of the present invention is provided with: a pair of convex-concave helical rotor that will rotate freely is accommodated in the interior compressor main body of housing; Be arranged at empty amount adjusting apparatus this compressor main body suction port, that control suction air quantity is used; The gas holder that is connected and is provided with the exhaust port of above-mentioned compressor main body; Be connected with this gas holder, the oil separator that will separate away from the oil the pressurized air that compressor main body is discharged, this oil-flooded screw compressor, in the cylinder barrel of the housing of taking in above-mentioned helical rotor, suction side at potted line nearby is equipped with first opening, the sealing line potted line of the capable convex-concave helical rotor that seals in the ban is in when beginning drain position, with the suction side distance of a groove width of this helical rotor is only arranged, on the other hand, also be equipped with second opening, the position of second opening is than the close more suction side of first opening, and than the also close side of discharging of potted line, when the sealing line is in the position of putting the suction air into when the back capable potted line of above-mentioned convex-concave helical rotor, the distance that this helical rotor groove width is arranged with it in the discharge side, first pipeline that fuel feeding is used is connected with this second opening, this first pipeline is connected with top position, gas holder oil sump bottom, on the other hand, second pipeline that condensed water reclaims usefulness is connected with gas holder oil sump bottom, the 3rd pipeline that oil reclaims usefulness is connected with the bottom of above-mentioned oil separator, by second pipeline is connected with first opening of above-mentioned housing with back, the 3rd pipeline interflow, store in the condensed water of gas holder oil sump bottom and be discharged in the compression space of compressor main body from second pipeline that condensed water reclaims usefulness by first opening, the compressed-air actuated heat of compression by high temperature is evaporated, outside pressurized air is discharged to gas holder, the therefore operation that can not need to extract out condensed water.Also have, as mentioned above, because the position of above-mentioned first opening is connected with exhaust port, and be connected with the compression space that is positioned at away from sucking action space, since with condensed water and from the separating oil that oil separator imports import to gas holder in the little action space of difference of pressure, so its changes in flow rate is little, because condensed water that all the time can will be quantitative imports, so the also kinetic equation loss of generation therefrom not.In addition, because condensed water is directed to the action space that will discharge at once, so the rubbish and the mud of sneaking in this condensed water can be discharged from exhaust port immediately, therefore can prevent the accident and the abrasion that produce because of engaging-in rubbish and mud, and because condensed water is directed to the compression space that the horse back that is under high temperature, the high pressure conditions will be discharged, so this condensation evaporation of water also can carry out effectively.And, because condensed water is to import to the compression space with the state that separates the oil phase mixing of oil sump by the 3rd pipeline, so can not reduce the helical rotor in the above-mentioned compression of formation space and the greasy property of cylinder barrel.Also have, as mentioned above, because above-mentioned second opening is arranged at the position that suction process has finished compression space afterwards, so can only pure oil be imported to the compression space by first pipeline from oil sump, really helical rotor and cylinder barrel are cooled off, lubricate, seal, thereby and pressurized air in the pure oil that is included in supply is expanded reduce the suction air quantity that is drawn into compressor in suction port.In addition, because only will not contain the pure oil of condensed water imports in the compression space, so the surface at helical rotor and cylinder barrel can form uniform oil film, can carry out good lubricated, and the sintering that the corrosion that produces because of condensed water also can not occur and produce because of insufficient lubrication.
The oil-flooded screw compressor of a second aspect of the present invention, owing to be arranged at above-mentioned second aperture position on the above-mentioned housing, be provided with the interval of width more than the helical rotor groove width apart from first aperture position, therefore, because pure oil is imported to importing condensed water compression space before, so in the compression space, before importing condensed water, can be on the surface of helical rotor and cylinder barrel, preliminary election forms oil film definitely, consequently can carry out the lubricated of helical rotor and cylinder barrel more well.
The oil-flooded screw compressor of a third aspect of the present invention, owing to be provided with throttle valve midway at above-mentioned second pipeline, can apply resistance to the condensed water of coming, limit with the corresponding discharge capacity of its generating capacity, can only separate out condensed water, make its high-efficiency evaporating at once by the high temperature compressed air that will discharge from the oil sump bottom force feed of gas holder.
The oil-flooded screw compressor of a fourth aspect of the present invention because the internal diameter that makes above-mentioned second pipeline less than the first pipeline internal diameter, can make the flow section of condensed water little, is not provided with throttle orifice etc. condensed water is evaporated in compression space full dose.
The oil-flooded screw compressor of a fifth aspect of the present invention, because the through oil hole at above-mentioned first pipeline that is communicated with above-mentioned oil sump is provided with the body that prevents that prevents to suck condensed water, can only import to the compression space with being provided with the pure oil of sneaking into condensed water, rubbish and mud etc.
Claims (5)
1. oil-flooded screw compressor comprises: will rotate freely a pair of convex-concave helical rotor and be accommodated in compressor main body in the housing; Be arranged at capacity regulating device this compressor main body suction port, that control suction air quantity is used; The gas holder that is connected and is provided with the exhaust port of above-mentioned compressor main body; The oil separator that is connected with this gas holder, will separates away from the oil the pressurized air that compressor main body is discharged, it is characterized in that: in the cylinder barrel of the housing of taking in above-mentioned helical rotor, suction side at potted line nearby is equipped with first opening, the sealing line is when the potted line of the convex-concave helical rotor that seals of row is in the beginning drain position in the ban, with the suction side distance of this helical rotor groove width only arranged; On the other hand, also be equipped with second opening, the position of second opening is than the close more suction side of first opening, and than the also close side of discharging of potted line, when the sealing line is in the position of putting the suction air into when the back capable potted line of above-mentioned convex-concave helical rotor, with discharge side the distance of this helical rotor groove width only arranged, first pipeline that fuel feeding is used is connected with this second opening, this first pipeline is connected with top position, gas holder oil sump bottom, on the other hand, second pipeline that condensed water reclaims usefulness is connected with gas holder oil sump bottom, the 3rd pipeline that oil reclaims usefulness is connected with the bottom of above-mentioned oil separator, with second pipeline and the 3rd pipeline interflow, be connected with first opening of above-mentioned housing then.
2. the oil-flooded screw compressor of putting down in writing as claim 1 is characterized in that: be arranged at above-mentioned second aperture position on the above-mentioned housing, be provided with the interval of width more than the helical rotor groove width apart from first aperture position.
3. as claim 1 or 2 oil-flooded screw compressors of being put down in writing, it is characterized in that: be provided with throttle valve midway at above-mentioned second pipeline.
4. as claim 1 or 2 oil-flooded screw compressors of being put down in writing, it is characterized in that: the internal diameter of above-mentioned second pipeline is littler than the internal diameter of first pipeline.
5. as claim 1 or 2 oil-flooded screw compressors of being put down in writing, it is characterized in that: the through oil hole at above-mentioned first pipeline that is communicated with above-mentioned oil sump is provided with the body that prevents that prevents to suck condensed water.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11939696A JP3456090B2 (en) | 1996-05-14 | 1996-05-14 | Oil-cooled screw compressor |
| JP119396/96 | 1996-05-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1165249A CN1165249A (en) | 1997-11-19 |
| CN1083537C true CN1083537C (en) | 2002-04-24 |
Family
ID=14760468
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97102361A Expired - Fee Related CN1083537C (en) | 1996-05-14 | 1997-01-30 | Oil cooling type screw compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3456090B2 (en) |
| CN (1) | CN1083537C (en) |
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| AU2005335899B2 (en) * | 2005-08-25 | 2011-06-09 | Ateliers Busch Sa | Pump housing |
| BE1017001A3 (en) * | 2006-03-07 | 2007-11-06 | Atlas Copco Airpower Nv | A RESERVOIR FOR A REPLACEMENT LIQUID OF AN APPARATUS AND AN APPARATUS, AND AN OIL SEPARATOR EQUIPPED WITH SUCH A RESERVOIR. |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4361417A (en) * | 1979-06-12 | 1982-11-30 | Hitachi, Ltd. | Oil-cooled compressor |
| EP0067949A2 (en) * | 1981-06-05 | 1982-12-29 | Bauer Schraubenverdichter Gmbh | Valve block for controlling the oil supply of a screw compressor |
| US4419865A (en) * | 1981-12-31 | 1983-12-13 | Vilter Manufacturing Company | Oil cooling apparatus for refrigeration screw compressor |
| JPH0943329A (en) * | 1995-07-26 | 1997-02-14 | Mitsubishi Electric Corp | Azimuth sensor |
-
1996
- 1996-05-14 JP JP11939696A patent/JP3456090B2/en not_active Expired - Lifetime
-
1997
- 1997-01-30 CN CN97102361A patent/CN1083537C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4361417A (en) * | 1979-06-12 | 1982-11-30 | Hitachi, Ltd. | Oil-cooled compressor |
| EP0067949A2 (en) * | 1981-06-05 | 1982-12-29 | Bauer Schraubenverdichter Gmbh | Valve block for controlling the oil supply of a screw compressor |
| US4419865A (en) * | 1981-12-31 | 1983-12-13 | Vilter Manufacturing Company | Oil cooling apparatus for refrigeration screw compressor |
| JPH0943329A (en) * | 1995-07-26 | 1997-02-14 | Mitsubishi Electric Corp | Azimuth sensor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3456090B2 (en) | 2003-10-14 |
| JPH09303279A (en) | 1997-11-25 |
| CN1165249A (en) | 1997-11-19 |
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