CN109404289A - rotary machine - Google Patents
rotary machine Download PDFInfo
- Publication number
- CN109404289A CN109404289A CN201710701301.0A CN201710701301A CN109404289A CN 109404289 A CN109404289 A CN 109404289A CN 201710701301 A CN201710701301 A CN 201710701301A CN 109404289 A CN109404289 A CN 109404289A
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- Prior art keywords
- rotating member
- oil
- face
- compressor
- shell
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- 239000000203 mixture Substances 0.000 claims abstract description 30
- 239000012530 fluid Substances 0.000 claims description 33
- 230000006835 compression Effects 0.000 claims description 32
- 238000007906 compression Methods 0.000 claims description 32
- 230000007246 mechanism Effects 0.000 claims description 26
- 230000002093 peripheral effect Effects 0.000 claims description 24
- 238000003860 storage Methods 0.000 claims description 8
- 230000009471 action Effects 0.000 claims description 5
- 238000005452 bending Methods 0.000 claims description 3
- 239000003921 oil Substances 0.000 abstract description 82
- 239000010687 lubricating oil Substances 0.000 abstract description 49
- 238000013459 approach Methods 0.000 abstract 1
- 238000005461 lubrication Methods 0.000 description 11
- 238000000034 method Methods 0.000 description 7
- 230000004048 modification Effects 0.000 description 7
- 238000012986 modification Methods 0.000 description 7
- 238000000926 separation method Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 239000000314 lubricant Substances 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000001351 cycling effect Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 2
- 125000004122 cyclic group Chemical group 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 235000013399 edible fruits Nutrition 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005303 weighing Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 239000010725 compressor oil Substances 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C29/026—Lubricant separation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention relates to a rotary machine including a housing, a rotary member, and a discharge member. The shell contains an oil-gas mixture. The rotating member is disposed within the housing and is rotatable about an axis of rotation to entrain the oil and gas mixture into a cyclonic flow, whereby the oil content of the oil and gas mixture is reduced as the oil and gas mixture approaches the rotating member under centrifugal force. The discharge member is provided on the housing and extends radially inward from the housing to a position where a content of the oil is equal to or less than a predetermined content. The rotary machine according to the present invention can control the circulation rate of the lubricating oil well.
Description
Technical field
The present invention relates to a kind of rotating machineries.
Background technique
The content of this part provides only background information relevant to the disclosure, may not constitute the prior art.
Compressor (such as screw compressor, rotor compressor etc.) generally includes compression mechanism, drive shaft and motor.Driving
Axis is by the bearing support in bearing block and is driven by motor and is rotated.The rotation of drive shaft drives the movable of compression mechanism in turn
Component (for example, rotor etc. of the dynamic vortex of screw compressor, rotor compressor) movement is thus to working fluid (for example, refrigeration
Agent) it is compressed.Each movable member of compressor is (for example, the rotor of the dynamic vortex of screw compressor, rotor compressor, axis
Hold) lubrication of lubricating oil is required to maintain the job stability and reliability of each movable member and entire compressor.
Therefore, the oil circulation system of compressor is the important component of compressor.
In compressor operation, lubricating oil is for example from oil sump quilt under the action of pressure difference or under the action of pump oil mechanism
It is delivered at each movable member of compressor to be just lubricated to maintain the normal operation of movable member to all parts,
Finally also it is back to oil sump.In addition, in the cyclic process of lubricating oil, it can also will be between the contact surface of all parts
Impurity is taken away to reduce abrasion, and the torrid zone of all parts generated by friction or electric current is walked.
In the cyclic process of lubricating oil, some lubricating oil can leave together compressor with working fluid.If left
The lubricants capacity of compressor is too big, compressor operating for a period of time after, the amount of the lubricating oil in oil sump gradually decreases, that is,
Oil level decline, cause the lubricants capacity in compressor to be not enough to maintain the normal operation of movable member, thus cause compressor without
Method works normally.So the oil level of the oil sump in compressor is maintained to be very important.On the other hand, as working fluid is arranged
The lubricating oil of compressor can be also attached in the coil pipe of such as condenser and evaporator out, to influence working fluid and surrounding sky
The heat exchange efficiency of gas.Therefore, compressor needs reasonably to control its lubricating oil circulation rate (also referred to as oil recycle ratio).Herein,
Oil recycle ratio can be understood as (quality) ratio of contained lubricating oil in the per unit working fluid of discharge compressor.
To control oil recycle ratio, gas and oil separating plant can be set within the compressor.However, due in the shell of compressor
Portion space is limited, it is therefore desirable for a kind of structure is simple, occupy little space but efficiency controls the compressor of oil recycle ratio higher.
Summary of the invention
It is an object of the present invention to provide a kind of rotating machineries, and structure is simple, occupy smaller space and can
Efficiently control oily cycle efficieny.
It is another object of the present invention to provide a kind of compressor, manufacture and assembly simplify, and cost is relatively low, Neng Gouhe
The oil recycle ratio of reason ground control compressor.
According to an aspect of the invention, there is provided a kind of rotating machinery, the rotating machinery include shell, rotating member and
Component is discharged.Gas mixture is accommodated in the shell.The rotating member is arranged in the shell and can surround
Rotation axis rotation is to drive the gas mixture to form tornado flow, thus under the action of the centrifugal force in the gas mixture
Oil content with smaller closer to the rotating member.Discharge component setting is on the housing and from described
The content that shell extends radially inwardly to the oil is less than or equal at the position of predetermined content.Rotating machinery according to the present invention can
Lubricating oil circulation rate is well controllled.
In some embodiments, the discharge component is located at the outer of the intracorporal end of the shell and the rotating member
There is preset distance, the ratio between the preset distance and the diameter of the round passing away that component is discharged between circumferential surface
Less than 1.5.
In some embodiments, between the diameter of the round passing away of the preset distance and the discharge component
Ratio is greater than 0.25.
In some embodiments, the ratio between the preset distance and the diameter of the round passing away is 0.4
To between 0.5.
In some embodiments, the rotating member has first axis end face and the second axial end in the axial direction
Face, the discharge component positioning is between the first axial position and the second axial position, wherein in the first axial position
The radial side of the passing away of the discharge component is located at the passing away of the first axis end face
The opposite radial other side be aligned with the first axis end face；The institute of the passing away described in the second axial position
State the radial other side be located at second axial end face the passing away the radial side with it is described
The alignment of second axial end face.
In some embodiments, the discharge component is positioned to substantially right with the axial central portion of the rotating member
It is quasi-.
In some embodiments, the end of the neighbouring rotating member of the discharge component is along perpendicular to the rotation
The horizontal direction of axis linearly extends, and the end face of the end is obliquely fixed relative to the outer peripheral surface of the rotating member
To.
In some embodiments, the end of the neighbouring rotating member of the discharge component is along the rotating member
Circumferential direction and/or edge are parallel to the vertical direction bending of the rotation axis.
In some embodiments, the outlet of the discharge component is oriented the direction of rotation towards the rotating member
Downstream side, the intracorporal gas mixture of shell via the outlet enter the discharge component.
In some embodiments, the rotating member has first axis end face and the second axial end in the axial direction
Face, the discharge component are located in the axially external of the first axis end face or second axial end face, and the row
Extending inwardly into positioned at the intracorporal end of the shell for component flushes or extends to institute with the outer peripheral surface of the rotating member out
State the radially inner side of the outer peripheral surface of rotating member.
In some embodiments, the rotating member is the form of cam, eccentric part or balance weight, the discharge component
For the form of exhaust pipe or passing away.
In some embodiments, rotating machinery further includes compression mechanism, drive shaft and motor.The compression mechanism is located at
In the shell and it is configured to compress working fluid.The drive shaft is suitable for driving the compression mechanism.The motor
Including stator and the rotor that can be rotated relative to the stator and it is configured to that the drive shaft is driven to rotate.The rotation structure
Part is arranged in the drive shaft or is arranged on the rotor.
In some embodiments, the rotating member is between the compression mechanism and the motor or positioned at institute
It states between motor and oil storage tank.
In some embodiments, the rotating machinery is high-pressure side screw compressor.
In said structure, since the rotating member in rotating machinery is able to drive gas mixture shape around when rotated
At tornado flow, lubrication can be isolated from gas mixture under the action of the centrifugal force before gas mixture leaves compressor
Oil, lubricating oil circulation rate is well controllled.On the one hand, the oil level of oil sump in compressor can be maintained at aspiration level.
On the other hand, can make to leave the lubricants capacity reduction that compressor enters in compressor assembly, for example, making to enter in heat exchanger
Lubricants capacity reduces, to improve the whole work efficiency of compressor assembly.
Detailed description of the invention
By description referring to the drawings, the feature and advantage of one or several embodiments of the invention will become more
Add and be readily appreciated that, in which:
Fig. 1 is the longitudinal section view of the compressor including gas and oil separating plant of embodiment according to the present invention；
Fig. 2 is the cross-sectional view of the gas and oil separating plant of the compressor of Fig. 1；
Fig. 3 is the schematic diagram of the gas and oil separating plant of Fig. 1, the radial position of difference it illustrates exhaust pipe relative to balance weight
It sets；
Fig. 4 is the schematic diagram of the gas and oil separating plant of Fig. 1, the axially different position it illustrates exhaust pipe relative to balance weight
It sets；
Fig. 5 and Fig. 6 is the schematic diagram of the compressor with the gas and oil separating plant being located at different location；
Fig. 7 is the curve graph for showing the distance between exhaust pipe and balance weight and cycling rate；
Fig. 8 a is the oil and gas distributing map in the cross-sectional section of gas and oil separating plant according to the present invention；
Fig. 8 b is the oil and gas distributing map in the cross-sectional section of the gas and oil separating plant of comparative examples；
Fig. 9 is the schematic diagram similar with Fig. 2, and it illustrates a modifications of exhaust pipe；And
Figure 10 is the Longitudinal cross section schematic of the gas and oil separating plant of compressor, and it illustrates another modifications of exhaust pipe.
Specific embodiment
Description related to the preferred embodiment is only exemplary below, and is definitely not to the present invention and its application or usage
Limitation.The same reference numerals are used to designate identical components in various figures, therefore the construction of same parts will not
Repeat description.
For ease of description, being referred in the case where some component can be around rotation axis rotation herein for the component
" longitudinal direction " or " axial direction " refer to the direction parallel with rotation axis, and " radial direction " then refer to perpendicular to
The direction of rotation axis.The words such as " first " mentioned in this article, " second " are only used for distinguishing different components, are not intended to table
Show sequence or other meanings.
With reference to the accompanying drawings to describe gas and oil separating plant according to the present invention and including the compression of gas and oil separating plant
Machine.High-pressure side vertical vortex is shown in the figure, however, it should be understood that the present disclosure additionally applies for other types of
Compressor, for example, horizontal type scroll compressor, rotor compressor, piston compressor etc..
Referring to Fig.1, compressor 10 includes shell 11, the compression mechanism 12 being arranged in shell 11, motor 13 and drive shaft
(being referred to as rotary shaft or crankshaft) 14.
Motor 13 includes being fixed on the stator 13b of shell 11 and on the inside of stator 13b and being fixed on turning for drive shaft 14
Sub- 13a.When motor 13 starts, rotor 13a rotates and drive shaft 14 is driven to rotate together.
Drive shaft 14 and 12 matched together of compression mechanism are with 12 pairs of compression mechanism work of driving when drive shaft 14 rotates
Fluid (usually gaseous state) is compressed.In screw compressor 10 shown in the figure, the eccentric crank pin 14b of drive shaft 14 matches
To drive dynamic vortex 12b to rotate in the dynamic vortex 12b of compression mechanism 12.
Compressor 10 further includes the main bearing seat 15 for being fixed on shell 11.Main bearing seat 15 is via base bearing 15a to driving
Axis 14 carries out rotation support, and is supported to compression mechanism 12, particularly dynamic vortex component 12b.
Compression mechanism 12 includes being fixed to the determine vortex component 12a of shell 11 or main bearing seat 15 and relative to determine vortex portion
The dynamic vortex component 12b that part 12a can be moved.Under the driving of drive shaft 14, dynamic vortex component 12b is relative to determine vortex component
The movement of 12a moving (that is, the central axis of dynamic vortex component is moved around the central axis of determine vortex component, but dynamic vortex component
It itself will not be rotated around the central axis of itself).In the helical blade of determine vortex component 12a and the spiral of dynamic vortex component 12b
A series of compression chamber that volumes are gradually reduced from radial outside to radially inner side is formed between blade.Working fluid is in these compressions
Through overcompression in chamber, then it is discharged by the exhaust outlet 17 of compression mechanism 12.The exhaust outlet 17 of compression mechanism 12 is generally arranged at
The approximate centre of the end plate of determine vortex component 12a.
During screw compressor operation, the centrifugal force or centrifugal moment that eccentric part is rotated and generated will lead to compressor
Vibration.Eccentric part institute is balanced in general, balance weight is arranged on rotary part to provide reversed centrifugal force or centrifugal moment
The amount of unbalance of generation.In compressor 10 shown in Fig. 1, balance weight 110 is fixed on the outer peripheral surface of drive shaft 14 and neighbour
Nearly main bearing seat 15, balance weight 210 be arranged in the rotor 13a of motor 13 on the end face of compression mechanism 12, balance weight 310
Be arranged in the rotor 13a of motor 13 on the end face of compression mechanism 12.Although the compressor in figure includes three balance weights,
It is to be understood, however, that the quantity of balance weight can change according to concrete application demand.
In the example of compressor shown in Fig. 1, there is the storage for storing lubricating oil in the bottom of compressor housing 11
Oil groove 20.It could be formed with the lubricating oil substantially in its axially extending channel 14a, oil storage tank 20 in drive shaft 14 to pass through
Channel 14a be supplied to supporting surface between each bearing, main bearing seat 15 and dynamic vortex component 12b of compressor, with
And the components such as compression mechanism.After all parts to compressor are lubricated, lubricating oil can be back to oil storage tank 20.
As shown in Figure 1, compressor 10 is high-pressure side screw compressor.Exhaust pipe (discharge component) is provided on shell 11
130.Pressure working fluid is directly fed to compressor by the air entry (not shown) of air inlet pipe (not shown) and compression mechanism
In the suction chamber or low pressure chamber of structure 12, the shell of compressor is then discharged to through overcompression and from the exhaust outlet of compression mechanism 12 17
In 11 spaces surrounded.In the example shown in the series of figures, exhaust pipe 130 be sealably mounted in shell 11 so as to by compressed gas from
It is discharged in compressor 10.In the operational process of compressor, the working fluid being discharged from exhaust outlet 17 is mixed with lubricating oil, due to
The movement of the components such as rotor 13a of dynamic vortex component 12b, motor 13 can also make the lubrication supplied from the channel 14a of drive shaft 14
Oil is with the formal distribution of mist of oil in the space in compressor housing 11.Therefore, to the high pressure from the discharge compressor of exhaust pipe 130
Usually contain lubricating oil in working fluid, it is therefore desirable to which the profit in the working fluid of compressor is discharged via exhaust pipe 130 for control
Lubricating oil amount is to control the oil recycle ratio (OCR) of entire compressor.
In order to which the oil recycle ratio (OCR) of compressor is well controllled, gas and oil separating plant can be set in compressor 10.
However, the gas and oil separating plant being additionally arranged needs to occupy certain space, and complicate manufacture and assembling process.Especially exist
In the limited situation in the inner space of compressor, be not suitable for that gas and oil separating plant is extraly arranged.
In order to overcome the problems referred above, present inventor contemplates a solution, can use in compressor
Some components and only and reasonably configuring the relative positional relationship between each component using centrifugal force from high-pressure work
Lubricating oil is isolated in fluid and will be contained and is reduced content, the working fluid discharge even without containing lubricating oil, thus reasonably
Control the oil recycle ratio (OCR) of compressor.Such solution can significantly reduce amount of parts, save installation sky
Between, simplify assembling process, so as to greatly reduce cost.
The gas and oil separating plant of embodiment according to the present invention is described referring to Fig. 1 and Fig. 2.As shown, oil gas
Separator includes balance weight 110 and exhaust pipe 130.Balance weight 110 is fixed on the outer peripheral surface of drive shaft 14 and can be with
Drive shaft 14 rotate together.In this example, the rotation axis of balance weight 110 is also the rotation axis of drive shaft 14, that is, is driven
The longitudinal center axis of moving axis 14.Exhaust pipe 130 positioned at the outside of balance weight 110 and is sealingly fixed in radial directions
On shell 11.
Balance weight 110 has neighbouring and the outer peripheral surface 111 in face of exhaust pipe 130, first axis end face 115 relative to each other
With the second axial end face 117.Referring to FIG. 1, FIG. 2 and FIG. 3, balance weight can have radially radially protruding part outstanding
112 and the axial projection 114 that is axially extended from the second axial end face 117.It should be understood that the structure of balance weight is (special
It is not position, the size and number etc. of protruding portion) it can be changed according to concrete application situation.For example, balance weight can only have
There are any one of radially protruding part and axial projection.Extraly or alternatively, balance weight can have from first axle
The axial projection axially extended to end face.
When balance weight 110 rotates together with drive shaft 14, the radially protruding part 112 of balance weight 110 and axially projecting
The surrounding gas mixture being discharged from exhaust outlet 17 can be stirred and the gas mixture of surrounding is forced to form rotation by portion 114
It is distinguished and admirable.Under the influence of centrifugal force, the lubricating oil in gas mixture is radially outward got rid of to shell 11 and in gravity
Under back downward into along shell 11 into oil storage tank 20.In this way, the lubrication oil content in the gas mixture of balance weight 110
It is less, and the lubrication oil content in the gas mixture of shell 11 is then higher.Along from balance weight 110 to the side of shell 11
To the lubrication oil content in gas mixture increases.Lubrication oil content in the gas mixture of the radially inner side of tornado flow is small
Lubrication oil content in the gas mixture of the radial outside of tornado flow.Therefore, inventor proposes exhaust pipe being located at shell
Intracorporal end is located in the range of the tornado flow as caused by the rotation of balance weight, and the diameter for being especially located at tornado flow is inside
In the part of side.The expectation of the lubricating oil in the gas mixture to be discharged can be predefined according to desired oil recycle ratio
Content.It is then possible to determine the position of exhaust pipe according to predetermined expectation content (also referred to as " predetermined content ").Also
It is to say, exhaust pipe can be extended radially inwardly to the content of the lubricating oil in gas mixture from shell less than or equal to described pre-
Determine at the position of content.
It should be understood that inventive concept of the invention, which is based on tornado flow caused by balance weight 110 rotates, makes balance weight 110
Lubricating oil concentration gradients change between shell 11 principle and pass through opposite position between exhaust pipe 130 and balance weight 110
Relationship is set to obtain and it is expected reduced oil recycle ratio.In existing some compressors, due to installation requirements, exhaust pipe can also be stretched
Enter a segment length in compression case body, but in this case, as long as the built-in length of exhaust pipe meets installation requirement, therefore
Exhaust pipe protrudes into end often closer to compressor housing.In addition, in existing some compressors, due to lubricating oil along
The inner surface of compressor housing flows, therefore exhaust pipe can also protrude into a segment length in compression case body and flow into avoid lubricating oil
In exhaust pipe.However, the built-in length of the exhaust pipe in existing compressor setting and balance weight rotation, rotated by balance weight
The tornado flow of generation etc. is unrelated.
In one embodiment, inventive concept according to the present invention can be by exhaust pipe 130 in shell 11 and balance weight
Balance weight 110 is positioned closer between 110.Preferably, exhaust pipe 130 is arranged adjacent to balance weight 110, that is, be located in phase
Just will meet the lubricating oil containing reduction amount needed, not contain even at the preset distance of outer peripheral surface away from balance weight 110
The working fluid of lubricating oil is discharged.
Referring to figs. 2 and 3, exhaust pipe 130 is circular tubular member, and has round passing away 133.Exhaust pipe
130 also have the end face 131 of neighbouring balance weight 110.In other words, exhaust pipe 130 is located at the intracorporal end face 131 of shell from shell
Wall extends inwardly near balance weight 110.Have one between the end face 131 of exhaust pipe 130 and the outer peripheral surface 111 of balance weight 110
Set a distance L.It is desirable that, distance L can either be conducive to that working fluid is discharged via exhaust pipe 130, and can guarantee to be discharged
Working fluid in the lubricating oil containing lower content.Distance L can be determined according to operating condition, for example, balance weight 110 turns
Speed, environmental pressure, the distance of balance weight 110 to shell 11, containing via the lubricating oil in the working fluid of the discharge of exhaust outlet 17
The expectation content of lubricating oil etc. in amount, the working fluid being discharged via exhaust pipe 130.Distance L can be predetermined, or
Person can change according to the operating condition of compressor.Preferably, it is expected that the end face 131 of exhaust pipe 130 be positioned as close to it is flat
The outer peripheral surface 111 of weighing apparatus block 110 it is expected the end face 131 of exhaust pipe 130 simultaneously and is put down to provide preferably oil gas separation
The distance between the outer peripheral surface 111 of weighing apparatus block 110 should not flow area that is too small and adversely reducing exhaust pipe 130.
" lubricating oil of lower content " mentioned in this article or " lubricating oil for reducing content " etc. are referred to via exhaust pipe
Content of the content of lubricating oil in the working fluid of 130 discharges less than the lubricating oil in the working fluid in compressor housing 11
And in the range of suitable lubricating oil circulation rate (OCR).For ease of description, herein by the " work in compressor housing
Fluid " is known as " working fluid before separation " or " gas mixture ", and " working fluid being discharged via exhaust pipe 130 " is claimed
For " working fluid after separation ".
In the example of fig. 3, it is assumed that the diameter of round passing away 133 is D, then the ratio L/D of distance L and diameter D can
To be less than about 1.5.In some examples, the ratio L/D of distance L and diameter D can be greater than about 0.25.In some examples, away from
Ratio L/D from L and diameter D can be between about 0.25 to 1.25, between about 0.4 to 1, between about 0.4 to 0.75, preferably
Between about 0.4 to 0.5.It is highly preferred that the ratio of distance L and diameter D can be about 0.5.Referring to Fig. 7, it illustrates when compression
Machine is with the curve graph of the distance between exhaust pipe and balance weight and cycling rate when 5400RPM (rpm) operation.In Fig. 7,
Abscissa indicates the radial distance L between the end face of exhaust pipe and the outermost periphery of balance weight, and wherein D indicates exhaust pipe
Internal diameter；The oil recycle ratio OCR of ordinate expression compressor.As shown in fig. 7, the oil recycle ratio of compressor is most when L is about 1/2D
It is low, about 1.08%.For compressor in the prior art, when compressor is run with 5400RPM, oil recycle ratio is more than
5%.In contrast, in the present invention, by the way that exhaust pipe is arranged adjacent to balance weight, that is, by by exhaust pipe and balance weight
The distance between setting in a certain range, the oil recycle ratio of compressor can be reduced significantly, achieve and significant expect not
The technical effect arrived.
Inventor is tested Conventional press and compressor according to the present invention, and test result is listed in
In following table.Test is for one group of Conventional press (C1) and three groups of compressors (T1, T2 and T3) of the present invention in difference
It is carried out under operating condition (different rotating speeds of balance weight), wherein the ratio of distance L and diameter D are 0.4 in compressor of the present invention.
Test result in table is the content of the lubricating oil in the working fluid after separation.In Conventional press C1, exhaust pipe is only
It is protruded into compressor housing for assembling convenience, but far from balance weight, that is, exhaust pipe is much larger than at a distance of the distance of balance weight
The internal diameter of exhaust pipe.
| Revolving speed (RPM) | T1 | T2 | T3 | C1 |
| 3600 | 0.42% | 0.41% | 0.37% | 1.29% |
| 5400 | 0.96% | 1.13% | 0.57% | 5.54% |
| 6000 | 1.77% | 1.77% | 1.24% | 7.56% |
According to the test result in above-mentioned test and table it is found that the workflow being discharged from compressor according to the present invention
Content of the content of lubricating oil in body significantly lower than the lubricating oil from the working fluid that Conventional press is discharged.The test knot
Fruit shows that liquid-gas separation device of the invention can efficiently isolate lubricating oil from gas mixture.Therefore, of the invention
Compressor significantly reduces the cycling rate (OCR) of lubricating oil.This is that Conventional press is not pre- in this field before the present invention makes
The effect that phase arrives.
It is the oil gas point in the cross-sectional section of gas and oil separating plant according to the present invention referring also to Fig. 8 a and Fig. 8 b, Fig. 8 a
Butut；And Fig. 8 b is the oil and gas distributing map in the cross-sectional section of the gas and oil separating plant of comparative examples.It can be seen that from Fig. 8 b
Nearby there is the lubrication higher region of oil content in balance weight outer peripheral surface, there is also lubrication oil content is higher near compressor housing
Region, the content of lubricating oil contained in the working fluid of exhaust pipe discharge is higher.In contrast, lubricating oil contains in Fig. 8 a
Measure higher region and concentrate on housing adjacent, therefore, in the working fluid of the exhaust pipe discharge of neighbouring balance weight setting containing compared with
A small amount of lubricating oil, to reduce the oil recycle ratio of compressor.
In compressor of the invention, balance weight forces the oil of surrounding as driving rotary member, and in its rotation
Gas mixture forms tornado flow, thus under the influence of centrifugal force radially throws away the biggish lubricating oil of specific gravity.As a result,
Contain less lubricating oil in the working fluid at balance weight, and is easy to from the exhaust pipe row being arranged from balance weight
Out.
In another embodiment, the end face 131 of exhaust pipe 130 can be on the rotation axis direction of balance weight 110
It is not parallel with the outer peripheral surface 111 of balance weight 110, but can outer peripheral surface towards balance weight 110 and relative to balance weight 110
111 inclinations.In alternative embodiment, the outlet of exhaust pipe 130 can be oriented the direction of rotation towards balance weight
Downstream side, wherein the gas mixture in compression case body enters in exhaust pipe via outlet and is discharged by exhaust pipe
Compressor.So, it is possible to reduce into the amount of the lubricating oil in exhaust pipe 130, so as to realize better Oil-gas Separation effect
Fruit.
In some instances, exhaust pipe 130 can along the horizontal direction vertical with the rotation axis direction of balance weight 110 from
Compressor housing linearly protrudes into.The outer peripheral surface 111 of the end face 131 of exhaust pipe 130 towards balance weight 110 orients, and opposite
It is tilted in the outer peripheral surface 111 of balance weight 110.In this case, the end face 131 of exhaust pipe 130 and the center of exhaust pipe 130 are longitudinal
Angle between axis is greater than 0 degree but less than 90 degree.
In other examples, the end of the neighbouring balance weight 110 of exhaust pipe 130 can be along the circumferential direction side of balance weight 110
It bends to and/or along the vertical direction parallel with the rotation axis of balance weight 110.That is, exhaust pipe 130 may include being located at shell
Interior folded end.Folded end can be curved arcuate shape or can be bent with constant angle.
As shown in figure 9, the folded end 230 of exhaust pipe 130 is bent along the circumferential direction of balance weight 110.In an example
In, the outlet at the end face 231 of folded end 230 can be towards the downstream of the direction of rotation of balance weight 110.Thus, it is possible to
Realize better oil gas separation.
As shown in Figure 10, the folded end 330 of exhaust pipe 130 is along the vertical side parallel with the rotation axis of balance weight 110
To bending.In the example presented in the figure, the end face 331 of folded end 330 can be downwardly oriented.In alternative exemplary, folded end
330 end face 331 can be downwardly oriented or can along can reduce into the amount of the lubricating oil in exhaust pipe other are any
Suitable direction orientation.
On the axial direction of the compressor of diagram, caused by exhaust pipe 130 can be positioned at the rotation as balance weight 110
In the range of tornado flow.In the example depicted in fig. 4, it is axial to can be positioned at the first axial position P1 and second for exhaust pipe 130
Between the P2 of position.In the first axial position P1, exhaust pipe 130 is located at the axially external of the first axis end face 115 of balance weight 110
And it is substantially aligned with first axis end face 115.In other words, in the first axial position P1, the passing away 133 of exhaust pipe 130
Radial side be located at the axially external of first axis end face 115, and the opposite radial other side and first of passing away 133
Axial end face 115 is substantially aligned.According to the orientation in Fig. 4, in the first axial position P1, exhaust pipe 130 is upper in the axial direction
In the lower section of the first axis end face 115 of balance weight 110, and the axial topmost portion of the passing away of exhaust pipe 130 and the
One axial end face 115 is substantially aligned.In second axial position P2, exhaust pipe 130 is located at the second axial end face of balance weight 110
117 it is axially external and substantially aligned with the second axial end face 117.In other words, in second axial position P2, exhaust pipe 130
The radial other side of passing away be located at the axially external of the second axial end face 117, and the radial direction of passing away
Side and the second axial end face 117 are substantially aligned.According to the orientation in Fig. 4, in second axial position P2, exhaust pipe 130 is in axis
To on direction positioned at the top of the second axial end face 117 of balance weight 110, and the axial direction of the passing away of exhaust pipe 130 is most
Lower part and the second axial end face 117 are substantially aligned.
Imagination according to the present invention, exhaust pipe 130 can also be located in the first axial position P1 and second axial position P2
It respective axially external (that is, lower than the first axial position P1 or higher than second axial position P2) and can be in radial direction
It further extends internally on direction, for example extends to and flushed with the outer peripheral surface 111 of balance weight 110, or even extend to balance
The radially inner side of the outer peripheral surface 111 of block 110.The tornado flow due to caused by the rotation of balance weight 110 is discharged from exhaust pipe 130
Lower oil recycle ratio (OCR) can still be maintained in working fluid.
In the embodiment shown in Fig. 1 to Fig. 4, balance weight 110 is arranged on the outer peripheral surface of drive shaft 14.However, answering
Understand, gas and oil separating plant may include the balance weight and exhaust pipe being arranged on any other suitable revolving part.Example
Such as, as shown in figure 5, gas and oil separating plant may include the end face in face of compression mechanism that the rotor 13a of motor 13 is arranged in
Balance weight 210 on 1301.Referring to Fig. 6, gas and oil separating plant may include be arranged in motor 13 rotor 13a back to compression
Balance weight 310 on the end face 1302 of mechanism.Exhaust pipe 130 and the mutual alignment relation and size relationship of balance weight are referred to
Description above and properly set.
In the embodiment shown in Fig. 1 to Fig. 4, gas and oil separating plant is arranged between main bearing seat 15 and motor 13.
However, it should be understood that gas and oil separating plant can be set in any suitable of the inner space limited by compressor housing 11
Position at.For example, as shown in fig. 6, gas and oil separating plant can be between motor 13 and oil storage tank 20.
It is understood that balance weight can have any suitable structure, as long as balance weight can be rotated and be forced
The gas mixture of surrounding forms tornado flow.For example, balance weight can have the radial direction of constant radial dimension or variation
Size, and/or can have the axial dimension of constant axial dimension or variation.Balance weight can have cylinder-shaped periphery
Face, tapered outer circumferential surfaces or can be realized above-mentioned effect any other suitable shape outer peripheral surface.According to concrete application, in figure
Shown in balance weight by cam, eccentric part or any other suitable component of above-mentioned effect can be can be realized substitute.
Similarly, exhaust pipe can have any suitable structure and/or quantity, as long as it can be conducive to that work is discharged
Fluid.For example, exhaust pipe may include flared end.Exhaust pipe may include the outer peripheral surface inclination relative to balance weight
The end of ground setting.For example, the end of the neighbouring balance weight of exhaust pipe is downwardly inclined, it is advantageously possible on exhaust inside pipe wall in this way
Outflow of lubrication oil.Compressor in figure includes an exhaust pipe, however the quantity of exhaust pipe can be it is multiple.According to specifically answering
With exhaust pipe shown in figure can also be arranged on the substitution of the passing away in fixed structure.
Although some embodiments of the present invention and modification have had been described in detail, those skilled in the art should be managed
Solution the invention is not limited to being described above with embodiment shown in the drawings and modification but may include other various possibility
Modification and combination.For example, gas and oil separating plant can not have bottom, it is possible thereby to fall to lubricating oil directed along wall
In oil storage tank.It may be effected by one skilled in the art other modifications without departing from the spirit and scope of the present invention
And variant.All these modifications and variant are within the scope of the present invention.Moreover, all components described herein can be by
Equivalent component replaces in other technologies.
Claims (14)
1. a kind of rotating machinery, comprising:
Shell accommodates gas mixture in the shell,
Rotating member (110), the rotating member are arranged in the shell and can rotate around rotation axis to drive
The gas mixture forms tornado flow, thus under the action of the centrifugal force the content of the oil in the gas mixture with more leaning on
The nearly rotating member and it is smaller；And
It is discharged component (130), the discharge component setting extends radially inwardly to institute on the housing and from the shell
The content for stating oil is less than or equal at the position of predetermined content.
2. rotating machinery according to claim 1, wherein the discharge component is located at the intracorporal end of the shell and institute
Stating between the outer peripheral surface of rotating member has preset distance (L), the circle of the preset distance (L) and discharge component (130)
Ratio between the diameter (D) of shape passing away (133) is less than 1.5.
3. rotating machinery according to claim 2, wherein the circle of the preset distance (L) and discharge component (130)
Ratio between the diameter (D) of shape passing away (133) is greater than 0.25.
4. rotating machinery according to claim 3, wherein the preset distance (L) is straight with the round passing away
Ratio between diameter (D) is between 0.4 to 0.5.
5. rotating machinery according to claim 1, wherein the rotating member has first axle on rotation axis direction
To end face (115) and the second axial end face (117), the discharge component is located in the first axial position (P1) and the second axial position
It sets between (P2), wherein the radial side that the passing away of component is discharged described in the first axial position (P1) is located at
The opposite radial other side and the first axis end face of the passing away of the first axis end face
The radial other side of alignment, the passing away described in the second axial position (P2) is located at second axial end face
The radial side of the passing away be aligned with second axial end face.
6. rotating machinery according to claim 5, wherein the discharge component is positioned to the axial direction with the rotating member
Central portion is substantially aligned with.
7. rotating machinery according to claim 1, wherein the end edge of the neighbouring rotating member of the discharge component
Linearly extend perpendicular to the horizontal direction of the rotation axis, and the end face of the end is relative to the rotating member
Outer peripheral surface is obliquely oriented.
8. rotating machinery according to claim 1, wherein the end edge of the neighbouring rotating member of the discharge component
The circumferential direction of the rotating member and/or edge are parallel to the vertical direction bending of the rotation axis.
9. rotating machinery according to claim 1, wherein the outlet of the discharge component is oriented towards the rotation
The downstream side of the direction of rotation of component, the intracorporal gas mixture of shell enter the discharge component via the outlet.
10. rotating machinery according to claim 1, wherein the rotating member has first axis in the axial direction
End face (115) and the second axial end face (117), the discharge component are located in the first axis end face (115) or described
Two axial end faces (117) it is axially external, and it is described discharge component be located at the intracorporal end of the shell extend inwardly into
The outer peripheral surface of the rotating member flushes or extends to the radially inner side of the outer peripheral surface of the rotating member.
11. rotating machinery according to claim 1, wherein the rotating member is the shape of cam, eccentric part or balance weight
Formula, the discharge component are the form of exhaust pipe or passing away.
12. rotating machinery described in any one of -11 according to claim 1, further includes:
Compression mechanism (12), the compression mechanism are located in the shell and are configured to compress working fluid；
Drive shaft (14), the drive shaft are suitable for driving the compression mechanism；And
Motor (13), the motor include stator and the rotor that can be rotated relative to the stator and are configured to described in driving
Drive shaft rotation；
Wherein, the rotating member is arranged in the drive shaft or is arranged on the rotor.
13. rotating machinery according to claim 12, wherein the rotating member is located at the compression mechanism and the horse
Between reaching or between the motor and oil storage tank.
14. rotating machinery according to claim 12, wherein the rotating machinery is high-pressure side screw compressor.
Priority Applications (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710701301.0A CN109404289B (en) | 2017-08-16 | 2017-08-16 | Rotary machine |
| JP2020508359A JP2020531728A (en) | 2017-08-16 | 2018-07-19 | Rotation mechanism |
| PCT/CN2018/096240 WO2019033894A1 (en) | 2017-08-16 | 2018-07-19 | Rotary mechanism |
| KR1020207006830A KR20200040802A (en) | 2017-08-16 | 2018-07-19 | Rotating mechanism |
| EP18846743.5A EP3670918A4 (en) | 2017-08-16 | 2018-07-19 | ROTATING MECHANISM |
| JP2022163887A JP2022183232A (en) | 2017-08-16 | 2022-10-12 | Rotary mechanism |
| JP2023001406U JP3242528U (en) | 2017-08-16 | 2023-04-26 | rotation mechanism |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710701301.0A CN109404289B (en) | 2017-08-16 | 2017-08-16 | Rotary machine |
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| CN109404289A true CN109404289A (en) | 2019-03-01 |
| CN109404289B CN109404289B (en) | 2024-05-14 |
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| CN201710701301.0A Active CN109404289B (en) | 2017-08-16 | 2017-08-16 | Rotary machine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114198302A (en) * | 2022-01-27 | 2022-03-18 | 广东美的环境科技有限公司 | Scroll compressors and air conditioning systems |
| CN116412138A (en) * | 2021-12-29 | 2023-07-11 | 广东美的环境科技有限公司 | Compressor and temperature control equipment |
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| CN116412138A (en) * | 2021-12-29 | 2023-07-11 | 广东美的环境科技有限公司 | Compressor and temperature control equipment |
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