CN204755308U - Screw refrigerating system and screw compressor thereof - Google Patents
Screw refrigerating system and screw compressor thereof Download PDFInfo
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- CN204755308U CN204755308U CN201520564401.XU CN201520564401U CN204755308U CN 204755308 U CN204755308 U CN 204755308U CN 201520564401 U CN201520564401 U CN 201520564401U CN 204755308 U CN204755308 U CN 204755308U
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- 230000007246 mechanism Effects 0.000 claims abstract description 19
- 210000002421 cell wall Anatomy 0.000 claims description 27
- 238000006073 displacement reaction Methods 0.000 claims description 9
- 238000005057 refrigeration Methods 0.000 claims description 9
- 239000006200 vaporizer Substances 0.000 claims description 8
- 238000003825 pressing Methods 0.000 claims description 4
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 208000002925 dental caries Diseases 0.000 claims description 2
- 239000003921 oil Substances 0.000 description 35
- 230000006835 compression Effects 0.000 description 19
- 238000007906 compression Methods 0.000 description 19
- 230000001276 controlling effect Effects 0.000 description 13
- 239000007788 liquid Substances 0.000 description 11
- 239000003507 refrigerant Substances 0.000 description 9
- 230000000694 effects Effects 0.000 description 7
- 230000001105 regulatory effect Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 239000000314 lubricant Substances 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 0.000 description 4
- 239000000203 mixture Substances 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 239000010729 system oil Substances 0.000 description 3
- 230000003044 adaptive effect Effects 0.000 description 2
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 238000005247 gettering Methods 0.000 description 2
- 230000013011 mating Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000003134 recirculating effect Effects 0.000 description 1
- -1 screw compressor Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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Abstract
The utility model discloses a screw refrigerating system and screw compressor thereof, this screw compressor include that casing and intermeshing just rotationally set up a pair of negative and positive rotor in the casing, still include two guiding valves edge axial reciprocating motion's of energy guiding valve, volume guiding valve and separately -driven actuating mechanism, and admit air chamber and exhaust chamber are split into with the casing to the inner wall cooperation of energy guiding valve, volume guiding valve, negative and positive rotor and casing, the axial spout that is used for holding volume guiding valve is offered to the energy guiding valve, and the notch of spout extends to negative and positive rotor axial contacting line between them, air discharge duct, the notch orientation exhaust chamber and the contacting line of air discharge duct have been seted up to the volume guiding valve. Compared with the prior art, above -mentioned screw compressor has set up energy adjustment mechanism and has compared adjustment mechanism with inner volume, and can control inner volume very easily to partial load and compare, and then the matching that pressure ratio and external pressure compare in realizing, reduce part load overcompression or the under -voltage degree that contracts down to obtain the best part load performance.
Description
Technical field
The utility model relates to screw compressor capacity regulating structure Unloading Technology field in screw-type refrigerating system, particularly a kind of screw-type refrigerating system and screw compressor thereof.
Background technique
At present, the screw-type refrigerating system that the middle or small cold section of central air-conditioning system adopts, with its compact structure, the advantage such as size is little, operational reliability is high, quick-wear part is less, technical performance is stable, management maintenance is simple, in the refrigeration system product type selection of central air-conditioner, extremely pay attention to.
As shown in Figure 1, screw-type refrigerating system generally includes and flows to along the refrigeration working medium in figure shown in arrow " → " vaporizer 1, exhaust end base of oil injection threaded bolt formula compressor 2, oil separator 3, condenser 4 and the throttle valve 5 that are communicated with successively.Particularly, liquid refrigerant absorbs heat to evaporate and forms refrigerant vapour in vaporizer 1, this refrigerant vapour is inhaled in screw compressor, oil separator 3 is entered after the low pressure refrigerant vapor being mixed with lubricant oil being compressed to elevated pressures in its compression chamber, oil separator 3 is by after refrigerant vapour and lubricating oil separation, refrigerant vapour flows into condenser 4 and carries out condensation, and be back under the differential pressure action of lubricant oil between vaporizer 1 and condenser 4 in exhaust end base of oil injection threaded bolt formula compressor 2, with to bearing, rotors etc. lubricate, sealing, cooling, noise reduction, then lubricant oil is back to refrigerant vapour the circulation that oil separator 3 completes lubricant oil.The liquid refrigerant formed after condensation in condenser 4 is shunted, a part is back in vaporizer 1 and enters next refrigeration cycle after throttle valve 5 reduces pressure, another part flows in exhaust end base of oil injection threaded bolt formula compressor 2, for cooling for its drive motor, being back to equally after cooling motor in vaporizer 1 and participating in next refrigeration cycle.
Wherein, screw compressor 2 comprises casing, and the drive motor being connected to male rotor in this casing and female rotor rotationally by bearing and shaft seal and being driven male rotor to rotate, male rotor and female rotor axis being parallel arrange and engage each other.
Mostly be configured with capacity controlling gear in existing fuel injection helical lobe compressor and there is no that deploy content is long-pending compares controlling mechanism.When running at full capacity, compression function operates with the interior volume specific ratio of the best, but when changing load, interior volume specific ratio can change along with the action of capacity controlling gear.Although at this moment load there occurs change, outside operating conditions is substantially constant, and namely outer pressure ratio is substantially constant.The change of interior volume specific ratio changes directly causing interior compression end of a period pressure, and then causes the situation occurring overcompression or under-voltage contracting during compressed refrigerant vapor.
During under-voltage contracting, outlet pipe pressure is greater than interior compression end of a period pressure, inter-tooth volume is communicated with moment with vent ports, rapid retrograde flow enters in inter-tooth volume by the gas in vent ports, pressure wherein to be risen to rapidly outlet pipe pressure from interior compression end of a period pressure, constantly reduces Exhaust Gas then along with inter-tooth volume.
During overcompression, outlet pipe pressure is lower than interior compression end of a period pressure, inter-tooth volume is communicated with moment with vent ports, gas in inter-tooth volume can flow into vent ports rapidly, make pressure wherein be reduced to rapidly outlet pipe pressure from interior compression end of a period pressure, constantly reduce Exhaust Gas then along with inter-tooth volume.
Obviously, when external and internal pressure is than time unequal, always can cause aditional energy loss, and then cause compressor section load performance low, reduce the competitiveness of product in market.In addition, the violent disturbance that also can cause air-flow because external and internal pressure is unequal, produces strong periodic noise.
In view of this, those skilled in the art urgently improve the structure of existing screw compressor, to reduce the aditional energy loss and noise that cause because of under-voltage contracting or overcompression.
Model utility content
For above-mentioned defect, core object of the present utility model is, provides a kind of screw compressor, to solve the aditional energy loss and noise that existing mechanism causes because of under-voltage contracting or overcompression.On this basis, the utility model also provides a kind of screw-type refrigerating system comprising this screw compressor.
Screw compressor provided by the utility model, comprise casing and engage each other and be arranged at a pair negative and positive rotor in described casing rotationally, also comprise energy guiding valve, volume guiding valve and two driving mechanisms moving back and forth vertically of driving-energy guiding valve and volume guiding valve respectively, the inwall of energy guiding valve, volume guiding valve, negative and positive rotor and casing coordinates casing is divided into air-inlet cavity and exhaust cavity;
Energy guiding valve offers the axial slide for accommodating described volume guiding valve, and the notch of chute extends to the axial line of contact of both negative and positive rotors; Volume guiding valve offers air vent, and the notch of air vent is towards exhaust cavity and line of contact.
Compared with prior art, above-mentioned screw compressor is provided with capacity controlling gear and internal volume rate regulating mechanism, can be easy to control interior volume specific ratio for sub load, and then realize mating of inner pressure ratio and outer pressure ratio, the degree of overcompression or under-voltage contracting under minimizing sub load, decrease the energy loss because overcompression and under-voltage contracting cause and noise, thus obtain best part load performance.
Alternatively, described air vent comprises front cell wall, upper cell wall, left cell wall, right cell wall, and described front cell wall is obliquely installed to described exhaust cavity.
Alternatively, described energy guiding valve and described volume guiding valve are coordinated by suitable limited impression and positive stop lug boss, to limit both relative displacement relative displacements vertically vertically; In described limited impression and described positive stop lug boss, one is arranged at described energy guiding valve, and another one is arranged at described volume guiding valve.
Alternatively, described energy guiding valve and described casing are coordinated by suitable guide pad and guiding groove, with described energy guiding valve movement vertically of leading; In described guide pad and described guiding groove, one is arranged at described casing, and another one is arranged at described energy guiding valve.
Alternatively, described driver element comprises and to be slidably matched with the inwall of described casing and to form the piston of cavity, with the connecting rod for being connected described piston and described energy guiding valve or described capacity slide valve, described cavity is divided into the first cavity and the second cavity by described piston, described first cavity and one in described second cavity are used for being communicated with the pressurization passageway of pressure medium or relief passage, and another one is provided with Compress Spring.
Alternatively, described casing and described piston are provided with radial location boss, and described Compress Spring pre-pressing is between the two and be sheathed on respective positioning boss.
Alternatively, described casing comprise be fixedly connected sequentially along air flow direction front cover, suction end base, main casing, the housing that spues, exhausting end base and rear end cover, described suction end base, described main casing and the described housing that spues enclose formation rotor chamber, and described energy guiding valve and described volume guiding valve are positioned at described rotor chamber;
Described front cover and described suction end base enclose formation described cavity, the described housing that spues, described exhausting end base and described rear end cover, enclose and form cavity described in another, described energy guiding valve and described volume guiding valve described piston separately lay respectively in two described cavitys.
Except above-mentioned screw compressor, the utility model also provides a kind of screw-type refrigerating system, comprise and flow to along refrigeration working medium the vaporizer, screw compressor, oil separator and the condenser that are communicated with successively and form refrigeration cycle, wherein, described screw compressor is screw compressor as above.
Because this screw compressor has above-mentioned technique effect, be appreciated that the screw-type refrigerating system comprising this screw compressor has same technique effect, so again repeat no more herein.
Accompanying drawing explanation
Fig. 1 shows the structure principle chart of screw-type refrigerating system;
Fig. 2 shows the axial sectional structure schematic diagram of screw compressor provided by the utility model;
Fig. 3 shows energy guiding valve and the volume guiding valve assembly radial structure schematic diagram of screw compressor shown in Fig. 2;
Fig. 4 shows the radial structure schematic diagram of energy guiding valve;
Fig. 5 shows the rear side radial structure schematic diagram of volume guiding valve;
Fig. 6 shows the axial arrangement schematic diagram of volume guiding valve.
Corresponding relation in Fig. 1 between reference character and all parts title:
1 vaporizer, 2 screw compressors, 3 oil separators, 4 condensers, 5 reduction valve.
Corresponding relation in Fig. 2 to Fig. 6 between reference character and all parts title:
Casing: 11 front covers, 12 suction end bases, 12a energy liquid pressure passageway hole, 13 main casings, 14 spue housing, 15 exhausting end bases, 16 rear end covers, 16a volume hydraulic channel hole, A rotor chamber, B energy hydraulic pressure cavity, C volume hydraulic pressure cavity;
Capacity controlling gear: energy stop block, 25 energy stop blocks afterwards before cell wall, the left cell wall of 20a-2 first, the right cell wall of 20a-3 first, 20b energy guiding valve lower end surface, 20c guiding groove, limited impression 20d, 21 power piston, 22 energy connecting rods, 23 energy compression springs, 24 on 20 energy guiding valves, 20a chute, 20a-1 first;
Internal volume rate regulating mechanism: volume stop block before volume stop blocks, 35 after cell wall on cell wall, 30a-2 second, the left cell wall of 30a-3 second, the right cell wall of 30a-4 second, 30b positive stop lug boss, 30c volume guiding valve lower end surface, 31 volume pistons, 32 volume connecting rods, 33 volume Compress Springs, 34 before 30 volume guiding valves, 30a air vent, 30a-1;
4 guide pads.
Embodiment
Core of the present utility model is, provides a kind of screw compressor, normally adds unloading with what realize capacity adjusting mechanism, thus the Economy that improve when refrigeration system is run and reliability.On this basis, the utility model also provides a kind of screw-type refrigerating system comprising this screw compressor.
Next in conjunction with Figure of description, concrete structure and the working principle thereof of screw-type refrigerating system provided by the utility model and screw compressor is described.It should be noted that, composed component and the working principle of screw-type refrigerating system provided by the utility model are identical with prior art, those skilled in the art can realize completely based on prior art, so only described in detail the capacity controlling gear of its inventive point screw compressor and volume adjustment mechanism technology at this herein.
It should be noted that the noun of locality "front", "rear" occurred is with the air flow direction of screw compressor for benchmark sets herein, air-flow is front near inlet end, after exhaust end is then; " left side " and " right side " is be that benchmark sets with air flow direction equally, and be namely positioned at for left on the left of air flow direction, the right side being positioned at air flow direction is right; " axis " refers to the direction being parallel to described negative and positive rotor axis, and the not proper axial direction along female rotor or male rotor, and " radial direction " refers to perpendicular to above-mentioned axial plane, also namely perpendicular to the plane of both negative and positive rotors axis.
In addition; for the ease of understanding technological scheme better; address herein chute and air vent time the ordinal number " first " that adopts and " second " be only to be distinguished both; do not have other implications, namely the appearance of above-mentioned ordinal number does not limit protection domain of the present utility model yet.
Refer to Fig. 2, the figure shows the axial sectional structure schematic diagram of screw compressor provided by the utility model.
As shown in Figure 2, screw compressor comprises casing and to be rotatably installed in casing and intermeshing a pair negative and positive rotor, also comprise capacity controlling gear and internal volume rate regulating mechanism, casing is divided into air-inlet cavity and exhaust cavity by the inwall cooperation of capacity controlling gear, internal volume rate regulating mechanism, negative and positive rotor and casing.
Wherein, casing comprises front cover 11, suction end base 12, main casing 13, the housing 14 that spues, exhausting end base 15 and rear end cover 16 6 assemblies, and these six assemblies are set gradually along air flow direction and to be adjacently fixedly connected with by bolt assembly between the two.
Suction end base 12, main casing 13 and the housing 14 that spues enclose and form rotor chamber A, and negative and positive rotor is rotatably installed in rotor chamber A.
Capacity controlling gear comprises energy guiding valve 20 and energy spool actuation unit, energy guiding valve 20 is positioned at rotor chamber A and is positioned at above negative and positive rotor, and along being parallel to the direction of negative and positive rotor axis relative to casing to-and-fro motion under the effect of energy spool actuation unit, that is, energy guiding valve 20 is relative to casing to-and-fro motion vertically.
Composition graphs 3 and Fig. 4 known, energy guiding valve 20 offers the axial slide for accommodating volume guiding valve 30, and this chute comprises cell wall 20a-1 on first, the first left cell wall 20a-2 and the first right cell wall 20a-3, and three forms the axial line of contact of notch towards both negative and positive rotors of chute, match with the external frame of the volume guiding valve lower end surface 30c and negative and positive rotor that make volume guiding valve 30.
Except slide groove portion exceptionally, the energy guiding valve lower end surface 20b that energy guiding valve 20 radial cross-sectional shape also comprises one section of major arc and is made up of two sections of smoothed curves.Energy guiding valve 20 is slidably matched by the inwall of its major arc section and casing, these two sections of smoothed curves respectively with the two end part of major arc for starting point, axial line of contact to both negative and positive rotors extends downward in opposite directions and is connected with volume guiding valve lower end surface 30c, to form the arc surface matched with negative and positive rotor outer profile, then form complete compression chamber.
In addition, in order to ensure linear relative to casing axially reciprocating of energy guiding valve 20, suitable guiding groove 20c and guide pad 4 between energy guiding valve 20 and casing, is also provided with.
In detail, composition graphs 2 to Fig. 4 is known, and guiding groove 20c is opened in the major arc section of energy guiding valve 20 and extends vertically, and the top of guide pad 4 is held on main casing 13 and spues between housing 14, and its underpart is intercalated in the guiding groove 20c of energy guiding valve 20.
Like this, when energy guiding valve 20 is relative to casing axially reciprocating, can prevents energy guiding valve 20 from rocking relative to the circumference of casing along negative and positive rotor, ensure that functional reliability and the Security of capacity controlling gear.
Energy guiding valve 20 driver element comprises power piston 21, energy connecting rod 22 and energy compression spring 23, also comprises and encloses by front cover 11 and suction end base 12 the energy hydraulic pressure cavity B formed.
Particularly, suction end base 12 offers axial blind hole, and, offer the energy hydraulic communication holes 12a be communicated with this axial blind hole, front cover 11 static seal be fixed on suction end base 12 with and its axial blind hole enclose and form energy hydraulic pressure cavity B.
Power piston 21 is positioned at energy hydraulic pressure cavity B and is slidably matched with the axial motive sealing of its inwall, and energy hydraulic pressure cavity B is isolated into hydraulic pressure section and non-hydraulic section by power piston 21, and hydraulic pressure section is communicated with system pressure oil circuit or oil return circuit by energy liquid pressure passageway hole 12a.
Energy connecting rod 22 runs through suction end base 12 vertically, and one end is stretched into energy hydraulic pressure cavity B and is fixedly connected with power piston 21 by bolt assembly, and the other end is stretched in rotor chamber A and is connected with energy guiding valve 20.
Energy compression spring 23 in non-hydraulic section and pre-pressing between power piston 21 and front cover 11, move right to promote power piston 21 when hydraulic pressure section is communicated with oil return circuit (i.e. relief passage).
Further, power piston 21 and front cover 11 are provided with and extend in opposite directions vertically and the coaxial positioning boss arranged, and the two end part of energy compression spring 23 are sheathed on the positioning boss of power piston 21 and front cover 11 respectively.
Setting like this, can ensure the conformity in energy compression spring 23 elastic force direction on the one hand, can simplify the mounting process of energy compression spring 23 on the other hand.
In addition, in order to limit the displacement of energy guiding valve 20 relative to casing axially reciprocating, energy spool actuation unit also comprises the front energy stop block 24 and rear energy stop block 25 that are fixed on suction end base 12 and the housing 14 that spues respectively, to limit energy guiding valve 20 respectively relative to casing displacement amount forward and backward.
Continue known see Fig. 2, when the hydraulic pressure section of energy hydraulic pressure cavity B is communicated with system oil return oil circuit by energy liquid pressure passageway hole 12a, the oil return of hydraulic pressure section, power piston 21 promotes energy guiding valve 20 and moves backward under the resilient force of energy compression spring 23; Otherwise when the hydraulic pressure section of equivalent hydraulic pressure cavity is communicated with system pressure oil circuit by energy liquid pressure passageway hole 12a, the oil-feed of hydraulic pressure section, the elastic force that power piston 21 overcomes energy compression spring 23 under pressure oil liquid effect pulls promotion energy guiding valve 20 to move forward.
Continue composition graphs 2, Fig. 3 to Fig. 6 is known, internal volume rate regulating mechanism comprises volume guiding valve 30 and volume spool actuation unit, and volume guiding valve 30 is plugged in the axial slide 20a of energy guiding valve 20 movably.
In radial cross section, the external frame of volume guiding valve 30 comprises the chute suitable with the chute shape of energy guiding valve 20 and coordinates section and be connected two sections of smoothed curve sections that chute coordinates section, these two sections of smoothed curves coordinate section two end part for starting point with chute respectively, extend in opposite directions to intersect to the axial line of contact of female rotor and form volume guiding valve lower end surface 30c, to form complete gas compression chamber with the external frame Spielpassung of negative and positive rotor again after being connected with the energy guiding valve lower end surface of energy guiding valve 20.
In addition, offer air vent 30a at volume guiding valve 30, the notch of this air vent 30a is towards the axial line of contact of axial exhaust chamber harmonizing yinyang rotor.Suitable content long-pending than time, only need control volume guiding valve 30 and slide axially, also namely under the effect of volume slide valve driving mechanisms, drive volume guiding valve 30 to-and-fro motion vertically, adjust the length of thread engagement of its air vent 30a and negative and positive rotor.
Continue known see Fig. 5 and Fig. 6, this air vent 30a comprises cell wall 30a-2 on front cell wall 30a-1, second, the second left cell wall 30a-3 and the second right cell wall 30a-4, and, its front cell wall 30a-1 tilts to exhaust cavity, be convenient to the smoothness that air-flow is creeped along air vent 30a, prevent air-flow from impacting in air vent 30a and forming vibrations.
Further, in order to prevent volume guiding valve 30 relative to the displacement of chute 20a vertical direction, vertical limit structure is also provided with between the two.
Particularly, composition graphs 3 to Fig. 5 is known, first left cell wall 20a-2 of energy guiding valve 20 and the first right cell wall 20a-3 offers respectively the limited impression 20d that two levels extend in opposite directions, correspondingly, the left side wall of volume guiding valve 30 and right side wall all arrange two the positive stop lug boss 30b extended in opposite directions in the horizontal direction.Both energy guiding valve 20 and volume guiding valve 30 are coordinated by above-mentioned vertical limit structure, to limit the relative displacement vertically of both volume guiding valve 30 and energy guiding valve 20, and the reliability both then ensure that during relative movement and Security.
It should be noted that, on the basis meeting processing technology requirement, limited impression suitable in vertical limit structure and positive stop lug boss also can oppositely be arranged, and are also, limited impression 20d is arranged at volume guiding valve 30, and positive stop lug boss 30b is then arranged at the corresponding position of energy guiding valve 20.
Volume spool actuation unit comprises volume piston 31, volume connecting rod 32 and volume Compress Spring 33, also comprises and encloses by the housing 14 that spues, exhausting end base 15 and rear end cover 16 the volume hydraulic pressure cavity C formed.
Particularly, exhausting end base 15 offers axial hole, and the housing 14 that spues is fixedly connected with its two apertures static seal respectively with rear end cover 16, then encloses and forms energy hydraulic pressure cavity B.
Volume piston 31 is positioned at volume hydraulic pressure cavity C and is slidably matched with the axial motive sealing of its inwall, equally, volume hydraulic pressure cavity C is isolated into hydraulic pressure section and non-hydraulic section by volume piston 31, hydraulic pressure section is communicated with system pressure oil circuit or oil return circuit by volume hydraulic channel hole 16a, and this volume hydraulic channel hole 16a is opened on rear end cover 16.
Volume connecting rod 32 motive sealing vertically runs through the housing 14 that spues, and one end is stretched into volume hydraulic pressure cavity C and is connected by bolt assembly and volume piston 31, and the other end is stretched in rotor chamber A and is connected with volume guiding valve 30.Volume Compress Spring 33 in non-hydraulic section and pre-pressing between volume piston 31 and rear end cover 16, move right to promote volume piston 31 when the oil return of hydraulic pressure section.
Further, volume piston 31 and rear end cover 16 are provided with and extend in opposite directions vertically and the coaxial positioning boss arranged, and the two end part of volume Compress Spring 33 are sheathed on the positioning boss of volume piston 31 and rear end cover 16 respectively.
Setting like this, can ensure the conformity in volume Compress Spring 33 elastic force direction on the one hand, can simplify the mounting process of volume Compress Spring 33 on the other hand.
In addition, in order to defined volume guiding valve 30 is relative to the reciprocating displacement of casing, volume guiding valve 30 driver element also comprises front volume stop block 34 and rear volume stop block 35 respectively, with difference defined volume guiding valve 30 relative to casing displacement amount vertically.Wherein, front axle is specially the vertical plate of suction end base 12 to stop block, and rear axial stop block is fixed on the housing 14 that spues.
Continue known see Fig. 2, when the hydraulic pressure section of volume hydraulic pressure cavity C is communicated with system oil return oil circuit by holding volume hydraulic channel hole 16a, the oil return of hydraulic pressure section, volume piston 31 promotes volume guiding valve 30 and moves backward under the resilient force of volume Compress Spring 33; Otherwise when the hydraulic pressure section of volume hydraulic pressure cavity C is communicated with system pressure oil circuit by volume hydraulic channel hole 16a, the oil-feed of hydraulic pressure section, the elastic force that volume piston 31 overcomes volume Compress Spring 33 under pressure oil liquid effect pulls promotion volume guiding valve 30 to move forward.
To sum up, above-mentioned screw compressor is provided with capacity controlling gear and internal volume rate regulating mechanism, can be easy to control interior volume specific ratio for sub load, and then realize mating of inner pressure ratio and outer pressure ratio, the degree of overcompression or under-voltage contracting under minimizing sub load, decrease the energy loss because overcompression and under-voltage contracting cause and noise, thus obtain best part load performance.
In detail, when load needed for user reduces, pressure oil liquid is back in system oil return oil circuit from energy hydraulic pressure cavity B, power piston 21 moves backward under energy compression spring 23 and differential pressure action, reduce effective active length of rotor, thus reduce the gettering quantity of screw compressor, with the requirement of adaptive system low-load.
Now, although load reduces, operating conditions is substantially constant.Control recirculating oil quantity in volume hydraulic pressure cavity C, make the suitably movement backward of volume piston 31, and then the position of volume adjusted guiding valve 30, suitable with outer pressure ratio with inner pressure ratio under making sub load, to obtain the performance of the best.
Load increases needed for the user, pressure oil liquid enters energy hydraulic pressure cavity B, the elastic force that power piston 21 overcomes energy compression spring 23 under this pressure oil liquid effect moves forward, then volume guiding valve 30 is driven to move forward relative to casing, add effective active length of rotor, thus increase the gettering quantity of compressor, with the requirement of adaptive system high load.
Now, although load increases, operating conditions is substantially constant.By controlling the oil inlet quantity in volume hydraulic pressure cavity C, make volume piston 31 suitably movement forward, and then the relative position of volume adjusted guiding valve 30 and negative and positive rotor, suitable with outer pressure ratio with inner pressure ratio under making sub load, to obtain the performance of the best.
When user runs under full capacity, only need Suitable content long-pending than controlling mechanism for different operating modes; When user runs at large pressure reduction or worst cold case, volume hydraulic pressure cavity C oil return, the suitably movement backward of volume piston 31, volume guiding valve 30 also moves thereupon backward, and now helical-lobe compressor interior volume specific ratio increases; When user runs at low voltage difference or worst hot case, volume hydraulic pressure cavity C oil-feed, the suitably movement forward of volume piston 31,30, volume guiding valve moves forward thereupon, and now helical-lobe compressor interior volume specific ratio reduces.
Finally, it should be noted that, in this embodiment, in two driving mechanisms, the first cavity of both accommodating power piston 21 respectively and volume piston 31 and the second cavity are all set to hydraulic pressure cavity, to utilize the lubricant oil of screw compressor as pressure medium to promote the to-and-fro motion vertically in respective cavity of both energy guiding valve 20 and volume guiding valve 30, save and independently pressure medium system is set, thus reduce the improving cost of screw compressor entirety.
Certainly, driving mechanism also can adopt pressurized gas equal pressure medium as power source, configure corresponding pressurization passageway and discharge channel again, then realize driving-energy piston 21 and volume piston 31 drives energy guiding valve 20 and volume guiding valve 30 to-and-fro motion vertically respectively.
That is, when accommodating energy guiding valve 20 is communicated with respective pressurization passageway with the second cavity with the first cavity of volume guiding valve 30 respectively, the elastic force that power piston 21 and volume piston 31 drive energy guiding valve 20 and volume guiding valve 30 to overcome Compress Spring respectively moves axially along a direction; When not accommodating energy guiding valve 20 is communicated with respective pressurization passageway with the second cavity with the first cavity of volume guiding valve 30, the elastic force that power piston 21 and 31, volume piston drive energy guiding valve 20 and volume guiding valve 30 to overcome elastic element respectively moves axially along other direction.
The foregoing is only preferred implementation of the present utility model, do not form the restriction to the utility model protection domain.Any do within spirit of the present utility model and principle any amendment, equivalent to replace and improvement etc., all should be included within claims of the present utility model.
Claims (8)
1. a screw compressor, comprise casing and engage each other and be arranged at a pair negative and positive rotor in described casing rotationally, it is characterized in that, also comprise energy guiding valve (20) and volume guiding valve (30), and two driving mechanisms driving described energy guiding valve (20) and described volume guiding valve (30) to move back and forth vertically respectively, the inwall of described energy guiding valve (20), described volume guiding valve (30), described negative and positive rotor and described casing coordinates described casing is divided into air-inlet cavity and exhaust cavity;
Described energy guiding valve (20) offers the axial slide (20a) for accommodating described volume guiding valve (30), and the notch of described chute (20a) extends to the axial line of contact of described both negative and positive rotors; Described volume guiding valve (30) offers air vent (30a), and the notch of described air vent (30a) is towards described exhaust cavity and described line of contact.
2. screw compressor as claimed in claim 1, it is characterized in that, described air vent (30a) comprises front cell wall (30a-1), upper cell wall (30a-2), left cell wall (30a-3), right cell wall (30a-4), and the described exhaust cavity of described front cell wall (30a-1) is obliquely installed.
3. screw compressor as claimed in claim 1, it is characterized in that, described energy guiding valve (20) and described volume guiding valve (30) are coordinated by suitable limited impression (20d) and positive stop lug boss (30b), to limit both relative displacements vertically; Described limited impression (20d) and the middle one of described positive stop lug boss (30b) are arranged at described energy guiding valve (20), and another one is arranged at described volume guiding valve (30).
4. screw compressor as claimed in claim 1, it is characterized in that, described energy guiding valve (20) and described casing are coordinated by suitable guide pad (4) and guiding groove (20c), with described energy guiding valve (20) movement vertically of leading; Described guide pad (4) and the middle one of described guiding groove (20c) are arranged at described casing, and another one is arranged at described energy guiding valve (20).
5. the screw compressor as described in any one of Claims 1-4, it is characterized in that, described driver element comprises and to be slidably matched with the inwall of described casing and to form the piston of cavity, with the connecting rod for being connected described piston and described energy guiding valve (20) or described capacity slide valve (30), described cavity is divided into the first cavity and the second cavity by described piston, described first cavity and one in described second cavity are used for being communicated with the pressurization passageway of pressure medium or relief passage, and another one is provided with Compress Spring.
6. screw compressor as claimed in claim 5, it is characterized in that, described casing and described piston are provided with radial location boss, and described Compress Spring pre-pressing is between the two and be sheathed on respective positioning boss.
7. screw compressor as claimed in claim 5, it is characterized in that, described casing comprises the front cover (11), suction end base (12), main casing (13), the housing that spues (14), exhausting end base (15) and the rear end cover (16) that are fixedly connected sequentially along air flow direction, described suction end base (12), described main casing (13) and the described housing that spues (14) enclose and form rotor chamber (A), and described energy guiding valve (20) and described volume guiding valve (30) are positioned at described rotor chamber (A);
Described front cover (11) and described suction end base (12) enclose formation described cavity, the described housing that spues (14), described exhausting end base (15) and described rear end cover (16) enclose and form cavity described in another, and described energy guiding valve (20) and the respective described piston of described volume guiding valve (30) lay respectively in two described cavitys.
8. a screw-type refrigerating system, it is characterized in that, comprise and flow to along refrigeration working medium the vaporizer (1), screw compressor (2), oil separator (3) and the condenser (4) that are communicated with successively and form refrigeration cycle, it is characterized in that, described screw compressor (2) is specially the screw compressor described in any one of claim 1 to 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520564401.XU CN204755308U (en) | 2015-07-30 | 2015-07-30 | Screw refrigerating system and screw compressor thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520564401.XU CN204755308U (en) | 2015-07-30 | 2015-07-30 | Screw refrigerating system and screw compressor thereof |
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| Publication Number | Publication Date |
|---|---|
| CN204755308U true CN204755308U (en) | 2015-11-11 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520564401.XU Expired - Fee Related CN204755308U (en) | 2015-07-30 | 2015-07-30 | Screw refrigerating system and screw compressor thereof |
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| Country | Link |
|---|---|
| CN (1) | CN204755308U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110857690A (en) * | 2018-08-22 | 2020-03-03 | 汉钟精机股份有限公司 | Screw compressor |
| CN112033036A (en) * | 2020-08-17 | 2020-12-04 | 珠海格力电器股份有限公司 | Refrigerating system, control method and air conditioner |
| WO2021036470A1 (en) * | 2019-08-26 | 2021-03-04 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
-
2015
- 2015-07-30 CN CN201520564401.XU patent/CN204755308U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110857690A (en) * | 2018-08-22 | 2020-03-03 | 汉钟精机股份有限公司 | Screw compressor |
| WO2021036470A1 (en) * | 2019-08-26 | 2021-03-04 | 珠海格力电器股份有限公司 | Compressor and air conditioner |
| CN112033036A (en) * | 2020-08-17 | 2020-12-04 | 珠海格力电器股份有限公司 | Refrigerating system, control method and air conditioner |
| CN112033036B (en) * | 2020-08-17 | 2024-02-23 | 珠海格力电器股份有限公司 | Refrigerating system, control method and air conditioner |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Yongda road 265500 Shandong province Yantai Fushan hi tech Industrial Zone No. 720 Patentee after: EBARA REFRIGERATION EQUIPMENT & SYSTEMS (CHINA) Co.,Ltd. Address before: Yongda road 265500 Shandong province Yantai Fushan hi tech Industrial Zone No. 720 Patentee before: YANTAI EBARA AIR CONDITIONER Co.,Ltd. |
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| CP01 | Change in the name or title of a patent holder | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20151111 |