CN106194750B - Screw compressor - Google Patents

Screw compressor Download PDF

Info

Publication number
CN106194750B
CN106194750B CN201510216987.5A CN201510216987A CN106194750B CN 106194750 B CN106194750 B CN 106194750B CN 201510216987 A CN201510216987 A CN 201510216987A CN 106194750 B CN106194750 B CN 106194750B
Authority
CN
China
Prior art keywords
compression
screw compressor
sucking
bearing seat
lubricant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201510216987.5A
Other languages
Chinese (zh)
Other versions
CN106194750A (en
Inventor
马文瑞
于英林
董培龙
梁胜
崔永华
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Emerson Climate Technologies Suzhou Co Ltd
Original Assignee
Emerson Climate Technologies Suzhou Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Emerson Climate Technologies Suzhou Co Ltd filed Critical Emerson Climate Technologies Suzhou Co Ltd
Priority to CN201510216987.5A priority Critical patent/CN106194750B/en
Priority claimed from KR1020177033911A external-priority patent/KR101971819B1/en
Publication of CN106194750A publication Critical patent/CN106194750A/en
Application granted granted Critical
Publication of CN106194750B publication Critical patent/CN106194750B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The present invention relates to screw compressors.Screw compressor according to the present invention includes: compression mechanism, and compression mechanism is suitable for compression work fluid and including dynamic vortex component, determine vortex component and sucking window, and working fluid can flow into compression mechanism via sucking window;Driving mechanism, driving mechanism include drive shaft and are suitable for driving compression mechanism;Accessory is sucked, working fluid can flow into screw compressor and then can flow to compression mechanism via sucking accessory;And lubricating system, lubricating system include lubricant source and suitable for supplying lubricant from lubricant source to the compression mechanism fueller of compression mechanism.Compression mechanism fueller has fuel feeding duct, and the outflow opening in fuel feeding duct is located between the opening of sucking accessory and sucking window.According to the present invention it is possible to make at oil recycle ratio in the appropriate range under different compressors revolving speed and/or not homologous ray operating parameters.

Description

Screw compressor
Technical field
The present invention relates to screw compressors, more particularly, to a kind of moderate oil supply side in compression mechanism fueller Face has the screw compressor of improvements.
Background technique
Compressor (such as screw compressor) can be applied to such as refrigeration (freezing or refrigeration) system, air-conditioning system and heat In pumping system.Screw compressor includes the compression mechanism for compression work fluid (such as refrigerant), compression mechanism and then packet Include dynamic vortex component and determine vortex component.Screw compressor in the running, compression mechanism dynamic vortex component and determine vortex portion There are relative motions between part.In order to reduce abrasion and reduce power consumption, need to compression mechanism provide lubrication (such as supply lubrication Oil) to improve the friction between dynamic vortex component and determine vortex component, while generated oil film can also improve compression mechanism Leakproofness to improving volumetric efficiency etc..
In general, can be characterized with oil recycle ratio the lubricating oil carried by working fluid number, and correspondingly can be with The degree that lubricating oil is supplied to compression mechanism is indicated with oil recycle ratio.The excessive supply or very few supply of lubricating oil all can be to pressures The normal operation of contracting mechanism itself and system performance etc. adversely affect.For example, excessive oil recycle ratio can reduce system Heat exchange efficiency, and can make grease accumulation determine vortex component outlet and discharge recess portion at discharge valve assembly Around (such as HVE valve module) (the especially top of discharge valve assembly) and be screw compressor bring certain problems (such as The operational stability problem of discharge valve assembly and/or the exhaust integrity problem of compression mechanism).
In addition, for system used variable speed compressor (variable speed compressor need with different rotating speeds operated) and/or Person's system needs the case where with different parameters (especially different evaporating temperatures) operating, it is desirable to which providing one kind can be not Oil recycle ratio is not made with compressor rotary speed and/or not to locate compression mechanism fuel feeding in the appropriate range under homologous ray operating parameters Device.
Moreover, for constant speed compressor, it would also be desirable to provide a kind of can be suitable for different rotating speeds one The good compression mechanism fueller of the versatility of serial constant speed compressor, the compression mechanism fueller can be each constant speed Oil recycle ratio of the compressor under respectively different revolving speeds at offer in the appropriate range.
Here, it is noted that technology contents provided in this part are intended to facilitate those skilled in the art couple Understanding of the invention, and not necessarily constitute the prior art.
Summary of the invention
There is provided total summary of the invention in this part, rather than complete scope of the present invention or all features of the present invention is complete Face discloses.
It is an object of the present invention to provide a kind of with the compression that can be realized fuel feeding target and concept on demand with oil The screw compressor of mechanism fueller.
Having it is a further object of the present invention to provide one kind can join in different compressors revolving speed and/or not homologous ray operating It is several lower so that oil recycle ratio locates the screw compressor of compression mechanism fueller in the appropriate range.
The oil under low evaporating temperature/slow-speed of revolution can be effectively prevented and follow by having it is a further object of the present invention to provide one kind The screw compressor of the compression mechanism fueller for the case where ring rate is far beyond the expected range upper limit.
It is a further object of the present invention to provide a kind of precision with the adjusting that can fully improve oil recycle ratio and set Count the screw compressor of the compression mechanism fueller of freedom degree.
One or more of to achieve the goals above, according to the present invention, provide a kind of screw compressor, comprising: pressure Contracting mechanism, the compression mechanism are suitable for compression work fluid and including dynamic vortex component, determine vortex component and sucking window, works Making fluid can flow into the compression mechanism via the sucking window;Driving mechanism, the driving mechanism include drive shaft And it is suitable for driving the compression mechanism;Accessory is sucked, working fluid can flow into the scroll compression via the sucking accessory In contracting machine and then the compression mechanism can be flowed to;And lubricating system, the lubricating system include lubricant source and are suitable for Lubricant is supplied from the lubricant source to the compression mechanism fueller of the compression mechanism.The compression mechanism fuel feeding dress Set with fuel feeding duct, the outflow opening in the fuel feeding duct be located at the sucking accessory opening and the sucking window it Between.
According to the present invention, during screw compressor operating, when the lubricant from lubricant source is arranged from the opening of cross-drilled hole When out, the lubricant being discharged meets with the pressure working fluid sucked, and pressure working fluid is moistened a part Lubrication prescription is brought into compression mechanism.In this way, realizing the fuel feeding mesh on demand with oil (also that is, so-called needs are how many, taking how many away) Mark and concept.
Specifically, on the one hand, for example for slow-speed of revolution operating condition, and be not provided with for the active to compression mechanism fuel feeding The scheme of oil injection mechanism is compared, and can be increased oil recycle ratio and is in it in expected range.On the other hand, such as height turn For fast operating condition, it will not exceedingly increase oil recycle ratio (substantially only can slightly increase oil recycle ratio) and make its holding It is in expected range (for example, this is because lubricant is when the every moving one of compression mechanism is enclosed from dynamic vortex base at high speed The lubricant quality of plate discharge is opposite to become smaller).Thus, it is possible under different compressors revolving speed and/or not homologous ray operating parameters So that oil recycle ratio is located in the appropriate range.Particularly, the oil circulation under low evaporating temperature/slow-speed of revolution can be effectively prevented The case where rate is far beyond the expected range upper limit.It can thus be avoided excessively high oil recycle ratio causes lubricant accumulation being discharged It is that screw compressor brings stability and integrity problem around valve module.
In addition, according to the present invention, by the way that the counterbore with larger inner diameter is arranged, by the way that outlet opening is arranged and/or leads to Crossing setting, there is the internal diameter of through-hole and through-hole can fully improve the precision of the adjusting of oil recycle ratio with smaller plug And design freedom, so that compression mechanism fueller has more excellent versatility and applicability.
Detailed description of the invention
By description referring to the drawings, the feature and advantage of one or more embodiments of the invention will become more Add and is readily appreciated that, in the accompanying drawings:
Fig. 1 is the longitudinal section view for showing the screw compressor for applying compression mechanism fueller according to the present invention;
Fig. 2 is the dynamic vortex component for showing the compression mechanism fueller for being combined with first embodiment according to the present invention Longitudinal section view;
Fig. 3 is the cross for showing the compression mechanism for the compression mechanism fueller for being combined with first embodiment according to the present invention Cross-sectional view;
Fig. 4 is the screw compressor for showing the compression mechanism fueller for being combined with first embodiment according to the present invention The perspective view of a part;
Fig. 5 is the dynamic vortex component for showing the compression mechanism fueller for being combined with second embodiment according to the present invention Longitudinal section view;
Fig. 6 is the schematic diagram for showing the exemplary parameter range of exemplary refrigeration system;
Fig. 7 be show the screw compressor for applying the compression mechanism fueller according to the relevant technologies a part it is vertical Cross-sectional view;And
Fig. 8 is the sectional elevation for showing the compression mechanism for applying the compression mechanism fueller according to the relevant technologies.
Specific embodiment
With reference to the accompanying drawings, by illustrative embodiments, the present invention will be described in detail.To it is of the invention it is following in detail Thin description is definitely not to the present invention and its application or the limitation of purposes merely for the sake of illustration purpose.
Firstly, summarily description applies the screw compressor of compression mechanism fueller according to the present invention referring to Fig.1 Structure (Fig. 1 is the longitudinal section view for showing the screw compressor for applying compression mechanism fueller according to the present invention).
As shown in Figure 1, screw compressor 100 may include shell 110.Shell 110 may include the shell in substantially tubular Body ontology 112 is installed to the top cover 114 at the top of enclosure body 112 and is installed to the bottom cover of the bottom of enclosure body 112 116.The internal capacity IV of the restriction screw compressor 100 of shell 110.In addition, partition 119 is also provided in shell 110, So that partition 119 and top cover 114 limit higher-pressure region HR, (higher-pressure region HR is suitable for temporarily storing the high pressure to be discharged to outside compressor Working fluid), and partition 119 and enclosure body 112 and bottom cover 116 limit low-pressure area LR.In addition, the lubricant of such as lubricating oil It can be stored in the oil sump OR at the bottom of the internal capacity IV in shell 110.In the example shown in the series of figures, screw compressor is So-called low-pressure side screw compressor.
Screw compressor 100 can also include sucking accessory 194.In the example shown in the series of figures, screw compressor 100 can be adopted Designed with middle part air inlet, also that is, sucking accessory 194 be arranged on compressor axial direction it is substantially opposite with main bearing seat 180 At neat position.The low-temp low-pressure working fluid after evaporator evaporation can be sucked via sucking accessory 194 as a result, To be compressed in screw compressor 100.
Screw compressor 100 can also include driving mechanism 130.Driving mechanism 130 may include electric motor 132 and drive Moving axis 134.Electric motor 132 may include stator 137 and rotor 138.Stator 137 may be fixedly attached to enclosure body 112 inner peripheral wall, and rotor 138 can fixedly cover in drive shaft 134 integrally to rotate with drive shaft 134.It is driving Cam pin 139 can be set at the top end part of moving axis 134.Here, it should be understood that can also be using without electric motor Other driving mechanisms.
Screw compressor 100 can also include main bearing seat 180.Main bearing seat 180 may be fixedly attached to shell sheet The inner peripheral wall of body 112.For example, main bearing seat 180 can by its multiple radial protrusion being circumferentially spaced and fixedly It is connected to the inner peripheral wall of enclosure body 112, so that between main bearing seat 180 and the inner peripheral wall of enclosure body 112 (that is, Between the adjacent radial protrusion of main bearing seat 180) multiple main bearing seat channel PG are formed with for example to allow to be sucked into inside Pressure working fluid in volume IV passes through.Main bearing seat 180 is suitable for via the base bearing being arranged in main bearing seat 180 182 and support a part of drive shaft 134.
Screw compressor 100 can also include the compression mechanism CM suitable for compression work fluid (such as refrigerant).Compression Mechanism CM may include dynamic vortex component 150 and determine vortex component 160.In some instances, compression mechanism CM may be embodied as Asymmetric compression mechanism.
Dynamic vortex component 150 may include: substrate 152;It is upwardly extended from the radial central portion of the upper surface of substrate 152 Helical form moves scrollwork 154;And the hub 156 extended downwardly from the radial center portion of the lower surface of substrate 152.Dynamic vortex component 150 can be arranged in main bearing seat 180, and are axially supported to by main bearing seat 180 and are able to carry out moving.Cam pin 139 It can be drivingly coupled to and (be inserted into) hub 156 (such as via unloading bushing 190 and/or driving bearing).
Determine vortex component 160 may include: substrate 162;The helical form extended downwardly from the lower surface of substrate 162 determines scrollwork 164;Be formed in the approximate center of substrate 162 suitable for the outlet 166 that is connected to the central high pressure room of compression mechanism CM;With And it is formed in the recess portion 168 of the approximate center of substrate 162, recess portion 168 is located at the top of outlet 166 and is suitable for and outlet 166 are connected to and are suitable for being connected to higher-pressure region HR.Discharge valve assembly (such as HVE valve module) can be set in recess portion 168 192, to control the exhaust of compression mechanism CM.In the example shown in the series of figures, determining scrollwork 164 may include being located at outermost radial outside (annular) outer wall 164a, and circumferential position appropriate can be provided with compression mechanism sucking window in outer wall 164a SW, sucking window SW allow pressure working fluid to be sucked into compression mechanism CM.
Determine scrollwork 164 to be suitable for engaging with dynamic scrollwork 154, to limit a series of crescent working fluid accommodating chambers.This A little accommodating chambers may include: unclosed just in the lower sucking accommodating chamber SC of the pressure of air inlet;It is closed to be pressed The compressed container room that the pressure of contracting increases;And completed compression via outlet 166 and discharge valve assembly 192 into The central high pressure room of row exhaust.Sucking accommodating chamber SC is suitable for being connected to sucking window SW, so as to receive from sucking window SW The pressure working fluid of sucking.
Screw compressor 100 can also include each relative movement part (such as the compression mechanism being mainly used for compressor CM, base bearing 182, cam pin 139, unloading bushing 190 and driving bearing) lubricating system of lubrication is provided.Lubricating system can be with Bao Shi: oil sump OR (main lubricant source) as mentioned above;Being arranged in drive shaft 134 includes being located at drive shaft lower part The oil supply gallery of centre bore 135 and the eccentric orfice 136 positioned at drive shaft top;Lubricate cam pin 139, for temporarily storing lubrication Lubrication of the temporal persistence in main bearing seat 180 after cam pin 139, unloading bushing 190, driving bearing and/or base bearing 182 The lubricant reservoir area (secondary lubricant source) of agent;From such as lubricant reservoir area to the compressor of compression mechanism CM supply lubricant Structure fueller CO (is not shown in Fig. 1 but may refer to Fig. 2 and Fig. 5);And make lubricant from such as lubricant reservoir area It is back to the drainback passage of oil sump OR.It should be mentioned here that oil sump OR and/or lubricant reservoir area are as according to the present invention Lubricant source.
In some instances, lubricant reservoir area may include positioned at cam pin 193, unloading bushing 190 and/or drive shaft Lubricant reservoir area OA between the top end surface held and the lower surface of dynamic vortex substrate 152 and in hub 156.
When screw compressor 100 operates, electric motor 132 is powered and revolves rotor 138 integrally with drive shaft 134 Turn.At this moment, the cam pin 139 such as with drive shaft 134 being integrally formed also rotates, thus for example via unloading bushing 190 and/ Or drive bearing and drive hub 156, thus make dynamic vortex component 150 by such as cross slip-ring 199 and relative to determine vortex Component 160 carries out translation rotation, that is, moving (also that is, the axis of dynamic vortex component 150 is public relative to the axis of determine vortex component 160 Turn, but both dynamic vortex component 150 and determine vortex component 160 itself are not rotated around their own axis).Meanwhile from Main bearing seat 180 can be passed through then via suction along main bearing seat channel PG by sucking the pressure working fluid that accessory 194 sucks Enter window SW to enter in compression mechanism CM and (specially enter in sucking accommodating chamber SC).
As a result, from determining scrollwork 164 and each accommodating chamber that dynamic scrollwork 154 limits is mobile from radial outside to radially inner side Never closed sucking accommodating chamber SC, which becomes compressed container room again, in the process becomes central high pressure room (having maximum pressure), and Volume is gradually from large to small.In this way, the pressure in accommodating chamber also gradually rises, so that working fluid is by compression and finally from discharge Mouth 166 is expelled to higher-pressure region HR and then is expelled to outside compressor via discharge accessory (not shown).
At the same time, such as under the action of the centrifugal force generated by the rotation of drive shaft 134, lubricant can be from oil Pond OR be delivered to via oil supply gallery (specially centre bore 135 and eccentric orfice 136) lubricant reservoir area (such as lubricant storage Deposit area OA).Then, by compression mechanism fueller CO, it is stored temporarily in one of the lubricant in lubricant reservoir area OA Divide and be supplied to compression mechanism CM (such as the appropriate area for being supplied to sucking accommodating chamber SC), to be provided to compression mechanism CM Lubrication.Then, remaining lubricant being stored temporarily in lubricant reservoir area OA is back to oil sump OR by drainback passage.
The case where describing the compression mechanism fueller CO' according to the lubricating system of the relevant technologies referring to Fig. 6 to Fig. 8 (Fig. 6 is that schematic diagram, the Fig. 7 for the exemplary parameter range for showing exemplary refrigeration system are to show to apply according to the relevant technologies Compression mechanism fueller screw compressor a part longitudinal section view and Fig. 8 is to show and apply according to related skill The sectional elevation of the compression mechanism of the compression mechanism fueller of art).
Referring specifically to Fig. 7, the compression mechanism fueller CO' according to the relevant technologies includes: to connect with lubricant reservoir area OA Logical ingate 201';The outlet opening 203' being connected to the appropriate area of sucking accommodating chamber SC;And with ingate 201' and out The cross-drilled hole 205' of both oral pore 203' connection.Ingate 201', outlet opening 203' and cross-drilled hole 205' can be formed in dynamic vortex base In plate 152.In some instances, the aperture position at the upper surface for being opened on dynamic vortex substrate 152 of outlet opening 203' is set Be set to and enable: outlet opening 203' is that the inside of the radially inner side positioned at dynamic scrollwork 154 sucks accommodating chamber SC and is located at dynamic whirlpool Both outside sucking accommodating chambers of the radial outside of volume 154 fuel feeding, moreover, can be avoided the opening of outlet opening 203' in dynamic vortex It is in the moving period of component 150 in compressed container room so as to avoid the lubricant in compression mechanism fueller CO' Under the action of elevated pressures in compressed container room and it is back to lubricant reservoir area OA.
In this way, when screw compressor operating, since the pressure of lubricant reservoir area OA is higher than the pressure of sucking accommodating chamber SC Power (corresponds to suction pressure), and makes pressure since the volume for sucking accommodating chamber SC in the charging stage can be gradually increased It further decreases, therefore lubricant can be swimmingly conveyed to compression mechanism CM.
In addition, referring to Fig. 6, it can be seen that be for example related to freeze applications and the exemplary refrigeration system using variable speed compressor The range of speeds, condensation temperature range and evaporating temperature range.In addition, according to the inventor's study and experiment, work as evaporating temperature When being in -40 °F to 0 °F of range, it can for example ensure that the oil recycle ratio (OCR) that expectation oil film is formed in scrollwork end is 0.05% to 1%, and when evaporating temperature is in 0 °F to 45 °F of range, it can for example ensure to form the phase in scrollwork end The oil recycle ratio (OCR) for hoping oil film is 0.05% to 2%.In a certain experiment, R404A refrigerant and compressor can be used Structure discharge capacity is 23CC.
In addition, referring to table 1, it can be seen that the case where being not provided with for active oil injection mechanism to compression mechanism fuel feeding Under, when system mesoscale eddies compressor is set as -40/130 ° with 2400RPM low-speed running and system evaporating temperature/condensation temperature When F, oil recycle ratio is lower than expected range lower limit i.e. 0.05% for 0.03%.
In addition, referring to table 1, it can be seen that according to the relevant technologies, especially when system mesoscale eddies compressor is low with 2400RPM When speed operates and system evaporating temperature/condensation temperature is set as -40/130 °F or -20/90 °F, oil recycle ratio is much higher than the phase Hope range limit i.e. 1%, howsoever these three sizes are adjusted to A, B and C.Particularly, even if in A and B size quilt In the case where being set as only 1.0mm, each oil recycle ratio is still much higher than on expected range under low evaporating temperature/slow-speed of revolution Limit.Here, it should be understood that, it is intended to it is unmanageable for reducing the duct of the internal diameter smaller (such as less than 1.0mm) of oil recycle ratio It and is substantially impossible.
Table 1
It follows that being difficult to according to the compression mechanism fueller CO' of the relevant technologies in different compressors revolving speed and/or not Locate oil recycle ratio in the appropriate range.Particularly, oil follows under low evaporating temperature/slow-speed of revolution Ring rate is far beyond the expected range upper limit.In this way, for example, excessively high oil recycle ratio will lead to lubricant accumulation in dump valve It is that screw compressor brings certain problems around component 192.
The compression mechanism fuel feeding dress of the lubricating system of first embodiment according to the present invention is described referring to Fig. 2 to Fig. 4 (Fig. 2 is the dynamic vortex portion for showing the compression mechanism fueller for being combined with first embodiment according to the present invention to the case where setting CO Longitudinal section view, Fig. 3 of part are the compressor for showing the compression mechanism fueller for being combined with first embodiment according to the present invention The sectional elevation of structure and Fig. 4 is the vortex for showing the compression mechanism fueller for being combined with first embodiment according to the present invention The perspective view of a part of compressor).
Referring specifically to Fig. 2, the compression mechanism fueller CO of first embodiment may include: and lubricate according to the present invention The ingate 201 of agent storage area OA connection;And the cross-drilled hole 205 being connected to ingate 201.Ingate 201 and cross-drilled hole 205 can be with It is formed in dynamic vortex substrate 152.In some instances, ingate 201 is the axial hole in axial direction extended.However, can With conception, ingate 201 or relative to the inclined inclined hole of axial direction.In some instances, cross-drilled hole 205 is along compression The lateral aperture that machine radial direction extends.However, it is possible to conceive, cross-drilled hole 205 may be relative to radial direction (horizontal direction) Inclined inclined hole.It should be mentioned here that ingate 201 and cross-drilled hole 205 constitute fuel feeding duct according to the present invention.
Cross-drilled hole 205 can be the consistent hole of internal diameter, and be opened on the peripheral surface 152a of dynamic vortex substrate 152.One In a little examples, the internal diameter of cross-drilled hole 205 can be 3.3mm.
In a preferable example, aperture position (outflow opening position) quilt for being opened on peripheral surface 152a of cross-drilled hole 205 It is arranged in the flow path of sucked pressure working fluid.Particularly, aperture position is in sucking accessory 194 and inhales Enter between window SW.
In some instances, as shown in figure 3, aperture position is located at sucking accessory 194 (specifically in compressor circumferential direction The opening at the inner peripheral wall for being opened on enclosure body 112 to suck accessory 194) and suck between window SW, and/or Person, as shown in figure 4, aperture position is located axially between sucking accessory 194 and sucking window SW.
In some instances, in circumferential direction, aperture position is less than and sucking window SW at a distance from sucking accessory 194 Distance, and/or, in the axial direction, aperture position with sucking accessory 194 at a distance from be greater than with sucking window SW away from From.
Generally, along working-fluid flow path, aperture position can be less than and sucking at a distance from sucking accessory 194 The distance of window SW.By this set, it is advantageously implemented the fuel feeding target and concept on demand with oil.
In some instances, in circumferential direction, aperture position close to or be aligned in sucking accessory 194.
In some instances, the aperture position of cross-drilled hole 205, which is located at, is connected the opening for sucking accessory 194 with sucking window SW Connecting line on.
In the example shown in the series of figures, sucking accessory 194 is arranged in the axial direction substantially aligns with main bearing seat 180 At position.In a preferable example, sucking accessory 194 is arranged to align with main bearing seat channel PG.By this set, have Conducive to the introducing of pressure working fluid, and be conducive to make the lubricant being discharged from dynamic vortex substrate 152 with from sucking accessory 194 The pressure working fluid of sucking meets, to be advantageously implemented oil recycle ratio appropriate.However, it is possible to conceive, accessory 194 is sucked (such as so-called bottom inflow design) can also be arranged at other positions in the axial direction.
Referring to Fig. 5 description compression mechanism fueller CO of the lubricating system of second embodiment according to the present invention Situation (Fig. 5 be show the compression mechanism fueller for being combined with second embodiment according to the present invention dynamic vortex component it is vertical Cross-sectional view).
Referring to Fig. 5, the compression mechanism fueller CO of second embodiment and according to the present invention first is real according to the present invention The main distinction for applying the compression mechanism fueller CO of mode is: cross-drilled hole 205 may include being located at radial outside section Counterbore 205a, and the internal diameter of counterbore 205a can be greater than the internal diameter of remaining section of cross-drilled hole 205 (for example, counterbore 205a's is interior Diameter can be 5mm).In some instances, additionally, according to the present invention the compression mechanism fueller CO of second embodiment with The difference of the compression mechanism fueller CO of first embodiment also resides according to the present invention: further including and sucking accommodating chamber SC The outlet opening 203 (axial hole or inclined hole) of appropriate area connection.
The compression mechanism fueller CO of the lubricating system of the variation example of second embodiment according to the present invention is described below The case where.In this variant, it is provided with plug 207.Plug 207 be adapted to be coupled to counterbore 205a (such as by screw thread connect It connects).Through-hole 207a can be set in plug 207, and through-hole 207a can have internal diameter appropriate.In some examples In, the internal diameter of through-hole 207a can be less than the internal diameter of remaining section of cross-drilled hole 205.In other examples, the internal diameter of through-hole 207a It can be equal to or the internal diameter of remaining section of even greater than cross-drilled hole 205.
Compression mechanism fueller according to the present invention as a result, stores up during screw compressor operating when from lubricant When depositing the lubricant of area OA dynamic vortex substrate 152 is discharged from the opening of cross-drilled hole 205, initiatively makes lubricant be discharged and inhaled The pressure working fluid entered meets, and pressure working fluid is brought a part of lubricant in compression mechanism CM into.In this way, The fuel feeding target and concept on demand with oil (also that is, so-called needs are how many, taking how many away) realized.
Specifically, on the one hand, for example for slow-speed of revolution operating condition, and be not provided with for the active to compression mechanism fuel feeding The scheme of oil injection mechanism is compared, and can be increased oil recycle ratio and is in it in expected range.On the other hand, such as height turn For fast operating condition, it will not exceedingly increase oil recycle ratio (substantially only can slightly increase oil recycle ratio) and make its holding It is in expected range (for example, this is because lubricant is when the every moving one of compression mechanism is enclosed from dynamic vortex base at high speed The lubricant quality of plate discharge is opposite to become smaller).Thus, it is possible under different compressors revolving speed and/or not homologous ray operating parameters So that oil recycle ratio is located in the appropriate range.Particularly, the oil circulation under low evaporating temperature/slow-speed of revolution can be effectively prevented The case where rate is far beyond the expected range upper limit.It can thus be avoided excessively high oil recycle ratio causes lubricant accumulation being discharged It is that screw compressor brings stability and integrity problem around valve module.
Meanwhile it will fall downwards to oil sump OR from remaining lubricant that dynamic vortex substrate 152 is discharged, and in this mistake The component that the needs of such as cross slip-ring 199 etc lubricate can also be effectively lubricated in journey.
In addition, the compression mechanism fueller of second embodiment and its variation example according to the present invention: by the way that counterbore is arranged, It can contribute to reduce the speed of lubricant discharge dynamic vortex substrate and help to improve the misty injection of lubricant;By attached Outlet opening is set with adding, lubricant is allowed to be fed directly to sucking accommodating chamber SC i.e. compression mechanism CM to properly increase oily circulation Rate;And by the way that the plug with through-hole is alternatively arranged, the freedom degree of the adjusting of oil recycle ratio can be improved.
In short, the compression mechanism fueller of second embodiment and its variation example according to the present invention, has by setting The counterbore of larger inner diameter has the internal diameter of through-hole and through-hole can be smaller by setting outlet opening and/or by being arranged Plug, the precision and design freedom of the adjusting of oil recycle ratio can be fully improved so that compression mechanism fuel feeding fill Setting has more excellent versatility and applicability.
Referring again to table 1, it can be seen that for the compression mechanism fueller of second embodiment according to the present invention, no By being under low evaporating temperature/slow-speed of revolution or under high evaporating temperature/high revolving speed, each oil recycle ratio is in expected range It is interior.In addition, in this second embodiment, the lubricant being discharged from outlet opening 203 is generally seldom (to be especially not provided with plug In the case where 207), therefore, the experimental result of the oil recycle ratio substantially in table 1 is also applied for first embodiment.
Compression mechanism fueller according to the present invention is particularly suited for use in variable speed compressor, is particularly applied to freeze In the variable speed compressor of system.However, the good compression mechanism fueller of versatility according to the present invention is readily applicable to A series of constant speed compressors with different rotating speeds.
Compression mechanism fueller according to the present invention can allow a variety of different modifications.
Air-breathing window can be two or more, and/or, the outflow opening in fuel feeding duct can for two or more It is multiple.In addition, air-breathing window can also by with it is as described above be set to the annular outer wall 164a for determining scrollwork 164 in the way of not Same mode is formed.
The fuel feeding duct of compression mechanism fueller CO can be formed in other ways.For example, fuel feeding duct is formed in master In the peripheral wall of bearing block and be opened on main bearing seat peripheral wall peripheral surface, at this point, lubricant reservoir area (lubricant source) It may include main bearing seat for accommodating the recess of such as hub 150.In another example fuel feeding duct is embodied as directly prolonging from oil sump It extends to sucking accessory and sucks the oil pipe of the position between window.
In short, may include following advantageous scheme in screw compressor according to the present invention.
In screw compressor according to the present invention, the outflow opening, which is located at from the opening of the sucking accessory, to be extended to On the working-fluid flow path of the sucking window.
In screw compressor according to the present invention, along the working-fluid flow path, the outflow opening and institute The distance for stating the opening of sucking accessory is less than at a distance from the sucking window.
In screw compressor according to the present invention, the dynamic vortex component includes dynamic vortex substrate, and the fuel feeding Duct is formed in the dynamic vortex substrate.
In screw compressor according to the present invention, the outflow opening is open to the outer weekly form of the dynamic vortex substrate Face.
In screw compressor according to the present invention, the lubricant source includes lubricant reservoir area, the lubricant storage Deposit area be located at the drive shaft cam pin endface and its near and the fuel feeding duct include and the lubricant store up The cross-drilled hole with the outflow opening depositing the ingate of area's connection and being connected to the ingate.
In screw compressor according to the present invention, the cross-drilled hole includes the counterbore at radial outside section, and The internal diameter of the counterbore is greater than the internal diameter of remaining section of the cross-drilled hole.
In screw compressor according to the present invention, the compression mechanism fueller further includes plug, and the plug is suitable In being connected to the counterbore, and through-hole is provided in the plug.
In screw compressor according to the present invention, the internal diameter of the through-hole is less than the interior of remaining section of the cross-drilled hole Diameter.
In screw compressor according to the present invention, the compression mechanism fueller further includes and the compression mechanism The outlet opening that sucking accommodating chamber is connected to and is connected to the cross-drilled hole.
In screw compressor according to the present invention, the lubricating system further includes the fuel feeding being arranged in the drive shaft Channel, the lubricant source further include the oil sump at the bottom of the internal capacity of the screw compressor, and lubricant The lubricant reservoir area can be flowed to from the oil sump via the oil supply gallery.
In screw compressor according to the present invention, the determine vortex component includes annular outer wall, and the sucking window Mouth is arranged in the annular outer wall.
In screw compressor according to the present invention, the screw compressor further includes main bearing seat, the main bearing seat It supports a part of the drive shaft and supports the dynamic vortex component and the sucking accessory in screw compressor axial direction Side is upwardly arranged at the position substantially to align with the main bearing seat.
In screw compressor according to the present invention, the main bearing seat is prominent with multiple radial directions being circumferentially spaced Portion, the main bearing seat are fixedly connected to the internal perisporium of the enclosure body of the screw compressor by the radial protrusion Face so that be formed between the main bearing seat and the inner peripheral wall multiple main bearing seat channels and it is described sucking match Part is arranged to align with the main bearing seat channel.
In screw compressor according to the present invention, the screw compressor further includes main bearing seat, the main bearing seat It supports a part of the drive shaft and supports the dynamic vortex component and the fuel feeding duct is formed in the base bearing Seat peripheral wall in and be opened on the main bearing seat peripheral wall peripheral surface.
In screw compressor according to the present invention, the screw compressor is the speed change pressure being suitably employed in refrigeration system Contracting machine.
In present specification, the use of directional terminology "top", "bottom", "up" and "down" etc. is only merely for convenient for description Purpose should not be taken as restrictive.
Although referring to illustrative embodiments, invention has been described, but it is to be understood that the present invention is not It is confined to the specific embodiment be described in detail and shown in text, without departing from claims limited range the case where Under, those skilled in the art can make various changes to illustrative embodiments.

Claims (15)

1. a kind of screw compressor (100), comprising:
Compression mechanism (CM), the compression mechanism (CM) be suitable for compression work fluid and including dynamic vortex component (150), determine whirlpool Component (160) and sucking window (SW) are revolved, working fluid can flow into the compression mechanism via the sucking window (SW) (CM) in;
Driving mechanism (130), the driving mechanism (130) include drive shaft (134) and are suitable for driving the compression mechanism (CM);
It sucks accessory (194), working fluid can flow into the screw compressor (100) via the sucking accessory (194) And then the compression mechanism (CM) can be flowed to;And
Lubricating system, the lubricating system include lubricant source and suitable for supplying lubricant from the lubricant source to the pressure The compression mechanism fueller (CO) of contracting mechanism (CM),
Wherein, the compression mechanism fueller (CO) has fuel feeding duct (201,205), the fuel feeding duct (201,205) Outflow opening be located at it is described sucking accessory (194) opening and the sucking window (SW) between,
The outflow opening is located at the opening of sucking accessory (194) in the circumferential direction of the screw compressor (100) Between sucking window (SW) and the outflow opening is described positioned at extending to from the opening of sucking accessory (194) It sucks on the working-fluid flow path of window (SW).
2. screw compressor (100) according to claim 1, wherein along the working-fluid flow path, the stream It is open at a distance from the opening of sucking accessory (194) and is less than at a distance from the sucking window (SW) out.
3. screw compressor (100) according to claim 1, wherein the dynamic vortex component (150) includes dynamic vortex base Plate (152), and the fuel feeding duct (201,205) is formed in the dynamic vortex substrate (152).
4. screw compressor (100) according to claim 3, wherein the outflow opening is open to the dynamic vortex base The peripheral surface (152a) of plate (152).
5. screw compressor (100) according to claim 4, wherein
The lubricant source includes lubricant reservoir area, and the lubricant reservoir area is located at the cam pin of the drive shaft (134) (139) endface and its near, and
The fuel feeding duct (201,205) include the ingate (201) being connected to the lubricant reservoir area and with it is described enter The cross-drilled hole (205) with the outflow opening of oral pore (201) connection.
6. screw compressor (100) according to claim 5, wherein the cross-drilled hole (205) includes being located at radial outside area Counterbore (205a) at section, and the internal diameter of the counterbore (205a) is greater than the internal diameter of remaining section of the cross-drilled hole (205).
7. screw compressor (100) according to claim 6, wherein the compression mechanism fueller (CO) further includes Plug (207), the plug (207) are adapted to be coupled to the counterbore (205a), and are provided in the plug (207) logical Hole (207a).
8. screw compressor (100) according to claim 7, wherein the internal diameter of the through-hole (207a) is less than the cross The internal diameter of remaining section in hole (205).
9. screw compressor (100) according to claim 8, wherein the compression mechanism fueller (CO) further includes The outlet opening (203) for being connected to the sucking accommodating chamber (SC) of the compression mechanism (CM) and being connected to the cross-drilled hole (205).
10. the screw compressor according to any one of claim 5 to 9 (100), wherein the lubricating system further includes The oil supply gallery (135,136) being arranged in the drive shaft (134), the lubricant source further include being located at the scroll compression Oil sump at the bottom of the internal capacity (IV) of machine (100), and lubricant can via the oil supply gallery (135,136) from The oil sump flows to the lubricant reservoir area.
11. screw compressor (100) according to any one of claim 1 to 9, wherein the determine vortex component (160) Including annular outer wall (164a), and the sucking window (SW) is arranged in the annular outer wall (164a).
12. screw compressor (100) according to any one of claim 1 to 9, wherein
The screw compressor (100) further includes main bearing seat (180), and the main bearing seat (180) supports the drive shaft (134) a part and the dynamic vortex component (150) is supported, and
The sucking accessory (194) is arranged in substantially opposite with the main bearing seat (180) on screw compressor axial direction At neat position.
13. screw compressor (100) according to claim 12, wherein
The main bearing seat (180) has multiple radial protrusions being circumferentially spaced, and the main bearing seat (180) is by described Radial protrusion is fixedly connected to the inner peripheral wall of the enclosure body (112) of the screw compressor (100), so that in the master Multiple main bearing seat channels (PG) are formed between bearing block (180) and the inner peripheral wall, and
The sucking accessory (194) is arranged to align with the main bearing seat channel (PG).
14. screw compressor (100) according to claim 1 or 2, wherein
The screw compressor (100) further includes main bearing seat (180), and the main bearing seat (180) supports the drive shaft (134) a part and the dynamic vortex component (150) is supported, and
The fuel feeding duct is formed in the peripheral wall of the main bearing seat (180) and is opened on the main bearing seat (180) The peripheral surface of peripheral wall.
15. screw compressor (100) according to any one of claim 1 to 9, wherein the screw compressor (100) To be suitably employed in the variable speed compressor in refrigeration system.
CN201510216987.5A 2015-04-30 2015-04-30 Screw compressor Active CN106194750B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201510216987.5A CN106194750B (en) 2015-04-30 2015-04-30 Screw compressor

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201510216987.5A CN106194750B (en) 2015-04-30 2015-04-30 Screw compressor
KR1020177033911A KR101971819B1 (en) 2015-04-30 2016-02-29 Scroll compressor
US15/569,350 US10641269B2 (en) 2015-04-30 2016-02-29 Lubrication of scroll compressor
PCT/CN2016/074823 WO2016173319A1 (en) 2015-04-30 2016-02-29 Scroll compressor

Publications (2)

Publication Number Publication Date
CN106194750A CN106194750A (en) 2016-12-07
CN106194750B true CN106194750B (en) 2019-02-01

Family

ID=57457615

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201510216987.5A Active CN106194750B (en) 2015-04-30 2015-04-30 Screw compressor

Country Status (1)

Country Link
CN (1) CN106194750B (en)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1215806A (en) * 1997-10-27 1999-05-05 运载器有限公司 Improved lubrication systems for scroll compressors
CN202266436U (en) * 2011-09-16 2012-06-06 大连三洋压缩机有限公司 Mechanism for controlling oil output of variable-frequency compressor
CN204646671U (en) * 2015-04-30 2015-09-16 艾默生环境优化技术(苏州)有限公司 Scroll compressor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03105092A (en) * 1989-09-18 1991-05-01 Hitachi Ltd Oil feeding device for sealed type two-stage scroll compressor
JP2616094B2 (en) * 1990-02-14 1997-06-04 ダイキン工業株式会社 Scroll compressor
JPH11247772A (en) * 1999-01-08 1999-09-14 Zexel:Kk Scroll fluid machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1215806A (en) * 1997-10-27 1999-05-05 运载器有限公司 Improved lubrication systems for scroll compressors
CN202266436U (en) * 2011-09-16 2012-06-06 大连三洋压缩机有限公司 Mechanism for controlling oil output of variable-frequency compressor
CN204646671U (en) * 2015-04-30 2015-09-16 艾默生环境优化技术(苏州)有限公司 Scroll compressor

Also Published As

Publication number Publication date
CN106194750A (en) 2016-12-07

Similar Documents

Publication Publication Date Title
CN204646671U (en) Scroll compressor
KR101971819B1 (en) Scroll compressor
CN101449028A (en) Compressor with built-in expander
US9239054B2 (en) Scroll compressor with oil-cooled motor
JP5433604B2 (en) Scroll compressor
JP2002089446A (en) Displacement type fluid machine
CN104214093B (en) Variable speed scroll compressor
CN110520624A (en) Rotary compressor
CN204003477U (en) Horizontal compressor
JPH06264876A (en) Scroll compressor
CN106194750B (en) Screw compressor
JP5181532B2 (en) Fluid machine and refrigeration cycle apparatus including the same
JP2004060502A (en) Compressor
CN209244821U (en) Screw compressor
US6672852B1 (en) Lubricant filling device for scroll compressor
JP2005201171A (en) Lubricating mechanism of compressor
CN110552886A (en) Compressor with a compressor housing having a plurality of compressor blades
JP4720649B2 (en) Electric compressor
KR20180136282A (en) Compressor having centrifugation and differential pressure structure for oil supplying
CN208487016U (en) Compressor
JP2012215086A (en) Oil supply pump device of compressor
CN208996942U (en) Screw compressor
JP2005171911A (en) Scroll compressor
CN212643056U (en) Scroll compression mechanism and scroll compressor
JPWO2019044867A1 (en) Scroll compressor

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
GR01 Patent grant
GR01 Patent grant