CN203146401U - Direct-connected radial compressor and oil return apparatus thereof - Google Patents
Direct-connected radial compressor and oil return apparatus thereof Download PDFInfo
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- CN203146401U CN203146401U CN 201220151388 CN201220151388U CN203146401U CN 203146401 U CN203146401 U CN 203146401U CN 201220151388 CN201220151388 CN 201220151388 CN 201220151388 U CN201220151388 U CN 201220151388U CN 203146401 U CN203146401 U CN 203146401U
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Abstract
The utility model relates to a direct-connected radial compressor and an oil return apparatus thereof. A compressor casing disposed at the lower part of a sliding bearing arranged on a compressor motor rotor is provided with a recessed cavity, forming an oil return cavity. The front wall and the rear wall of the oil return cavity face towards the side of a first oil return cavity, forming an axial inner-concave structure to increase the volume of the oil return cavity. The inner-concave structure is designed to ensure that at least the upper-middle part of the oil return cavity has an axial width, larger than the installing width of a first sliding bearing. The direct-connected radial compressor and the oil return apparatus thereof is advantageous in that the total volume of the oil return cavity is increased; lubricating oil being thrown out due to the high-speed rotation of the radial compressor can be easily discharged; and the lubricating oil can be at first thrown in quite a large space to release energy and decelerate, and thereby the oil can rapidly flow back to the oil return cavity.
Description
Technical field
The utility model relates to a kind of oil back chamber structure of centrifugal compressor, relates in particular to a kind of oil return apparatus that is applicable to the sliding bearing of the centrifugal compressor that the motor direct connection drives, and also relates to the centrifugal compressor with this oil return apparatus simultaneously.
Background technique
Existing centrifugal compressor, all volume is less for the oil back chamber under its sliding bearing of influencing that is subjected to rotor length and runs up, especially the centrifugal compressor that drives for the motor direct connection is subjected to the volume problem of restriction oil back chamber of rotor length serious especially, more particularly the high-speed centrifugal compressor that drives for the motor direct connection that adopts sliding bearing.When rotor goes to high speed by low speed, the required lubricants capacity of sliding bearing significantly increases, require this moment oil return necessary smooth and easy especially, otherwise these high temperature greases that come out from sliding bearing can cause the oil level of bearing present position to rise, thereby bring following serious consequence: (1) since oil level than higher, bearing is immersed in the high temperature oil always, and this has just lost the effect of taking away the bearing heating amount by lubricant oil, is easy to cause the excessive and tile kilning of bearing shell local temperature rise; (2) when oil level covers bearing, oil level will be crossed the seal interface, can cause lubricant oil to leak in the motor cavity at motor rotor core place from oil back chamber by the sealing configuration of disk like this, thereby not only influence the Compressor Group performance, and can cause lubricant oil constantly to reduce, and then influence unit safety operation.
Above-mentioned negative consequence, we find to be mostly can not to adapt to owing to the oil back chamber volume is too small, and dredge oil amount that the big dredge oil amount of sliding bearing causes sliding bearing causes greater than bearing oil back chamber volume of living in, therefore need to increase motor front and back two bearings oil back chamber volume, make the dredge oil amount of oil back chamber volume greater than the place bearing, like this, the high temperature grease that comes out from sliding bearing flow to oil back chamber rapidly, make bearing away from high temperature grease, both guaranteed the lubricating status of bearing, guaranteed also that oil level was unlikely to cause oil leak to the seal interface.
In view of above problem, a kind of structural feature design that can especially have the centrifugal compressor that the motor direct connection of sliding bearing drives according to the centrifugal compressor characteristics, under the situation that does not influence original component function, neither cause rotor length to increase, not only can increase the volume of oil back chamber but also be unlikely the compressor oil back chamber device that causes the casing volume or weight to increase extremely urgent.
The model utility content
One of the purpose of this utility model is to overcome the problems referred to above that prior art exists, provide a kind of and can be applicable to the oil return apparatus of straight connection type centrifugal compressor sliding bearing and the straight connection type centrifugal compressor that adopts this kind oil return apparatus, this kind oil return apparatus designs at the structural feature of the centrifugal compressor that the motor direct connection drives, under the situation that does not influence original component function, neither cause rotor length to increase, can increase the oil back chamber volume again, and can not cause the compressor box volume or weight to increase, guarantee simultaneously can flow to oil back chamber rapidly and drain into fuel tank from the high temperature grease that bearing comes out, guarantee that thus oil level can not be dipped in the seal interface and prevent that lubricant oil is in the leakage of seal interface.
In order to realize above-mentioned purpose of the present utility model, the technological scheme and the technique effect that adopt are specific as follows:
The utility model relates to a kind of oil return apparatus for the straight connection type centrifugal compressor, this compressor has first sliding bearing that is installed between motor rotor core and the impeller, it makes compressor first casing that is positioned at this first sliding bearing bottom have a cavity and forms first oil back chamber, first casing has antetheca and rear wall at axial direction, the upper end of this antetheca is provided with preceding disk, should before disk be installed in the rotating shaft between impeller and first sliding bearing, have the sealing effect of isolation impeller and first sliding bearing; The upper end of rear wall is provided with rear disk, and this rear disk is installed in the rotating shaft between first sliding bearing and the electric machine iron core, has the sealing effect of isolating first sliding bearing and electric machine iron core; The common antetheca that constitutes described first oil back chamber of the antetheca of disk and described first casing before described, the rear wall of described rear disk and described first casing is common constitute described first oil back chamber rear wall and described before or after disk forming axial concave inward structure towards the first oil back chamber side, make described first oil back chamber have the axial width that width is installed greater than first sliding bearing at least in the middle and upper part of its first oil back chamber.
Further, disk is a complex disc before described, it comprises that one is fixed on the compressor drum and is fixed on the described compressor first casing antetheca with first disk and that rotor rotates and do not rotate with axle, be positioned at second disk that the first disk periphery and described antetheca are set together, two disks are combined together the oil gas that can realize between compressor refrigerant lateral lobe wheel and the tank side bearing isolates and sealing, preferably, first disk forms first concave inward structure and/or described second disk to the hole enlargement of bearing side at the ear end face of its bearing side and forms second concave inward structure at the ear end face of its bearing side.
Further, described second disk forms a radial flange with drift angle and hypotenuse at the top edge of second concave inward structure, and preferred, the drift angle width L of this radial flange is 0.5mm～2mm; Angle of inclination beta is 20 °～40 °; Hypotenuse height h is 2mm～5mm; And/or the outer shroud edge of the described first disk bearing side forms one towards the oily structure of getting rid of of first oil back chamber, preferred this gets rid of oily structure and stretched to first oil back chamber vertically by the outer shroud edge of the first disk bearing side, and form a disc that has a groove on inclined-plane, preferably, disc drift angle width L1:0.5～1.5mm; Get rid of oily angle γ: 10 °～30 °; Disc height h1:0.5～2mm; Inside grooves knuckle R:0.3～1.5mm.
Further, described rear disk comprises that one is fixed on the baffle plate on the described compressor box rear wall and is fixed on the 3rd disk that forms rotatable sealing on this baffle plate with compressor drum, preferably, the 3rd disk forms one at the front-end face of described bearing and has the 3rd concave inward structure on water conservancy diversion inclined-plane and/or described baffle plate by across forming recessed the 4th concave inward structure to baffle plate at the 3rd disk rear wall and described casing rear wall, preferably, described baffle plate also forms an axial ledge to the extension of clutch shaft bearing side vertically, and this axial ledge radial compaction is in the upper end of described rear wall.
Further, the antetheca of described compressor first casing rear wall that forms the 5th concave inward structure and/or described compressor first casing forms the 6th concave inward structure.
Further, the bottom of first oil back chamber removably is connected with first shrouding, and the drainback passage that first shrouding is provided with on the diapire of first through hole and described first casing is communicated with that oil return is discharged.
The utility model also relates to a kind of oil return apparatus for the straight connection type centrifugal compressor, the afterbody of its rotor is provided with second sliding bearing, second casing that is formed on second sliding bearing bottom has a cavity and forms second oil back chamber, described second casing has antetheca and rear wall in the axial direction, fixedly have on the antetheca of second casing and be sleeved on the 4th disk that has seal action on the rotor shaft, back shrouding is also fixedly arranged on the rear wall of second casing, the antetheca of described second casing, the common antetheca that constitutes second oil back chamber of the 4th sealed disc, the rear wall of described second casing, the common rear wall that constitutes second oil back chamber of back shrouding, and described the 4th sealed disc forms the 7th axial concave inward structure and/or the back shrouding forms the 8th axial concave inward structure in the second oil back chamber side in the second oil back chamber side, makes described second oil back chamber have the axial width that width is installed greater than second sliding bearing in top at least therein.
Further, the interior ring edge of described the 4th disk formation one has the radial flange of drift angle and hypotenuse, and preferred, this radial flange drift angle width L is 0.5mm～2mm; Angle of inclination beta is 20 °～40 °; Hypotenuse height h is 2mm～5mm.
Further, the antetheca of described second casing forms downward plane of inclination, and is preferred, and the angle of inclination of plane of inclination is α, 75 ° 〉=α 〉=15 °, is preferably 60 ° 〉=α 〉=30 °.
Further, above described second casing, also be provided with upper cover plate, the upper end of one end and the 4th disk is installed together, the upper end of the other end and described back shrouding is installed together, preferably, upper cover plate forms a radial flange to the extension of the second oil back chamber side, this radial flange is sleeved on the outside of second sliding bearing and forms the indent end face relative with the 4th disk, this end face produces the 9th concave inward structure, further preferred, upper cover plate forms the tenth concave inward structure towards the end face of second oil back chamber.
Further, described back shrouding forms a through hole, the sealing of through hole outer end liquid-sighting glass is installed, through hole and liquid-sighting glass are combined together described the 8th concave inward structure of formation.
Further, described second casing before or after wall form stairstepping.
Further, described second casing is formed with drainback passage in the bottom of second oil back chamber, and the bore of this drainback passage is less than the area of section of oil back chamber.
A kind of straight connection type centrifugal compressor, it has aforesaid oil return apparatus and/or aforesaid oil return apparatus.
Further, when it has aforesaid oil return apparatus and aforesaid oil return apparatus simultaneously, oil return in described second oil back chamber causes in first oil back chamber by first pipeline, the volume of the first casing cavity is more than or equal to first sliding bearing and the second sliding bearing dredge oil amount sum, further preferably, on level height, the end that described first pipeline links to each other with second casing is equal to or higher than the end that first pipeline links to each other with first casing; Perhaps, oil return in first oil back chamber causes in second oil back chamber by second pipeline, the volume of second oil back chamber is more than or equal to first sliding bearing and the second sliding bearing dredge oil amount sum, further preferably, on level height, the end that second pipeline links to each other with first casing is equal to or higher than the end that second pipeline links to each other with second casing; Perhaps, the oil return in the first casing cavity or the oil return in the second casing cavity are all directly drawn by pipeline and are back to fuel tank.
Further, described compressor is one or more levels impeller, and further preferred described multi-stage impeller is arranged on the cantilever end of rotor in the same way in turn.
Further, its rotor speed of straight connection type centrifugal compressor is more than 6000 rev/mins, and preferably more than 7000 rev/mins, further, described motor is the DC frequency-changing synchronous machine, and its power is between 150kW to 800kW.
Further, described sliding bearing is hydraulic bearing, further preferred, between the inner cylindrical surface of described hydraulic bearing and the rotor journal external cylindrical surface, the axial end of bearing and bearing is carried out all be formed with the oil groove that can produce the oil film kinetic pressure between the rotor radial flange end face of axially locating.
Description of drawings
Fig. 1 adopts the structural representation of oil return method one first, second oil back chamber of centrifugal compressor for the utility model;
Fig. 2 is the structure for amplifying schematic representation of the utility model first oil back chamber;
Fig. 3 a is the structural representation of the concave inward structure of the utility model second disk formation;
Fig. 3 b is the structure enlarged diagram of the radial flange that second disk forms among Fig. 3 a;
Fig. 3 c is the structure enlarged diagram of the radial flange drift angle that second disk forms among Fig. 3 b;
Fig. 4 a is the structural representation of the concave inward structure of the utility model the 3rd disk formation;
Fig. 4 b is the enlarged diagram of the concave inward structure that the 3rd disk forms among Fig. 4 a;
Fig. 5 is the concave inward structure that the utility model the 3rd disk and baffle plate form;
Fig. 6 a is the structure for amplifying schematic representation of the oil back chamber of the utility model second sliding bearing;
Fig. 6 b is the enlarged diagram of the concave inward structure that the 4th disk forms among Fig. 6 a;
Fig. 6 c is the structure enlarged diagram of the radial flange drift angle that the 4th disk forms among Fig. 6 b;
Fig. 7 adopts the structural representation of oil return method two for the utility model;
Fig. 8 adopts the structural representation of oil return method three for the utility model.
Reference character is as follows:
First sliding bearing (front slide bearing), 1, the first oil back chamber 1000;
The installation width W 2 of installation width W 1, the second sliding bearing of first sliding bearing;
Preceding disk 188; Second disk, 8, the first disks 18; Rear disk 910, the three disks 9, baffle plate 10;
First concave inward structure, 180, the first disks that first disk forms get rid of oily structure 181, get rid of the groove 1812 of oily structure, the inclined-plane 18121 of groove gets rid of the disc 1811 of oily structure;
The radial flange 81 of top edge 801, the second disks of second concave inward structure, 80, the second concave inward structures that second disk forms, the 4th concave inward structure 100 that baffle plate forms;
The water conservancy diversion inclined-plane 91 of the 3rd concave inward structure 90, the three disks that the 3rd disk forms;
The axial ledge 101 of baffle plate, the 4th concave inward structure 100 that baffle plate forms;
First through hole 5121 on first shrouding, 512, the first shroudings; First drainback passage 53 on first casing;
The 6th concave inward structure 520 that the 5th concave inward structure 510, the first casing rear walls that the first casing antetheca forms form;
Second sliding bearing (back sliding bearing), 2, the second oil back chambers 2000;
The radial flange 131 of the 7th concave inward structure 130, the four disks that the 4th disk 13, the four disks form;
Back shrouding 14, the 8th concave inward structure 140 that back shrouding forms, the through hole 141 on the back shrouding;
Upper cover plate 7, the 9th concave inward structure 70 that upper cover plate forms, the tenth concave inward structure 700 that upper cover plate forms;
The drainback passage 41 of second oil back chamber;
The downward plane of inclination 611 that the antetheca of radial flange 131, the second casings that the interior ring edge of liquid-sighting glass 15, the four disks forms forms, upper cover plate 7, the radial flange 71 of upper cover plate;
Embodiment
At first need to prove, in the terms such as the front end of the parts described in the utility model, front side, front before, distinguish according to the air current flow direction after in rear end, rear side, the back, before the airintake direction of air-flow is, after the outflow direction of air-flow is.The specific embodiment of this part, preferred feature just preferred embodiment shall not be construed as the unique restriction to the utility model institute mode of execution.
Below in conjunction with accompanying drawing 1-6 preferred embodiment of the present utility model is elaborated:
The utility model proposes two kinds of oil return apparatus, be applicable to the recovery of lubricant oil of the sliding bearing of forward and backward different installed positions respectively.Though some difference on both structures, both have all embodied such model utility design:
The structural feature design of the centrifugal compressor that drives at the motor direct connection, under the situation that does not influence original component function, utilize original structure to increase the oil back chamber volume by the mode that forms concave inward structure, special high speed characteristics at sliding bearing characteristics and straight connection type centrifugal compressor of while, we are special to propose, and concave inward structure will guarantee at least that the middle and upper part of oil back chamber has the axial width that width is installed greater than corresponding sliding bearing.Such design not only increases the total measurement (volume) of oil back chamber, the lubricant oil that also makes sliding bearing throw away in centrifugal compressor rotates at a high speed can easier be discharged, and can enter in the bigger space at the very start and release energy, speed reduces, thereby be beneficial to very fast being back in the oil back chamber of lubricant oil, this kind improvement, compare only by increasing the prior art that tank-volumes increases the refluxing chamber volume, though sacrificed the thickness as the parts of oil back chamber front and rear wall to a certain extent, but General strengthens greatly, this measure neither causes rotor length to increase, do not cause the compressor box volume or weight to increase again, but can make the high temperature grease that comes out from sliding bearing can flow to oil back chamber rapidly and be easy to discharge, thereby can not cause the oil immersion of oil back chamber to avoid the leakage of lubricant oil in the seal interface in the seal interface, the utility model improves the Security of rotor and bearing greatly, and the parts that constitute oil back chamber can be maximized the use.
Describe the following preferred embodiment that the utility model adopts below in detail.
As Fig. 1,2, because the utility model is particularly useful for the straight connection type centrifugal compressor, therefore the application that adopts of present embodiment is the straight connection type centrifugal compressor, and its impeller is installed in the cantilever end of rotor, and first sliding bearing 1 is between motor rotor core 3 and impeller 4.The position that arranges at first sliding bearing 1, the formation of first kind of oil return apparatus is: it makes compressor first casing 5 that is positioned at first sliding bearing, 1 bottom have a cavity 50 and forms first oil back chamber 1000, first casing 5 has antetheca 51 and rear wall 52 at axial direction, the upper end of antetheca 51 is provided with preceding disk 188, should before disk be installed in the rotating shaft between impeller 4 and first sliding bearing 1, have the sealing effect of isolating oil gas leakage between impeller 4 and first sliding bearing 1; The upper end of rear wall 52 is provided with rear disk 910, in the relatively turnable rotating shaft that is installed between first sliding bearing 1 and the motor rotor core 3 of this rear disk, has and isolates the sealing effect that oil is revealed between first sliding bearing 1 and the electric machine iron core.At the such structure of compressor, before not changing under the situation of the original position of disk and rear disk and effect, the utility model proposes, with the common antetheca that constitutes first oil back chamber of the antetheca of preceding disk and first casing, the common rear wall that constitutes first oil back chamber of the rear wall of rear disk and first casing, and before or after making disk (expressed concave inward structure is a kind of general name herein form axial concave inward structure towards first oil back chamber, 1000 sides, summary appellation for the concave inward structure that forms on each parts that constitutes first oil back chamber), thus the oil back chamber 1000 of winning is had in the middle and upper part of its first oil back chamber at least greater than first sliding bearing 1 installs the axial width of width W 1.
Preferably, as accompanying drawing 1, shown in 2, the utility model at the preceding disk 188 of compressor be a complex disc, it comprises that one is fixed on the compressor drum and is fixed on the above-mentioned compressor first casing antetheca 51 with first disk 18 and that rotor rotates and do not rotate with axle, be positioned at second disk 8 that first disk, 18 peripheries and antetheca 51 are set together, two disks are combined together the oil gas that can realize between compressor refrigerant lateral lobe wheel and the tank side bearing isolates and sealing, these effects are effects that complex disc itself has, for realizing the increase of first oil back chamber, the utility model is at this kind of complex disc formation situation, and special first disk 18 that proposes forms first concave inward structure 180 and/or described second disk 8 to the hole enlargement of bearing side at the ear end face of its bearing side and forms second concave inward structure 80 at the ear end face of its bearing side.Made thus complex disc many an effect that increases the oil back chamber volume.
For further increasing the oil back chamber volume, second disk 8 is designed to second concave inward structure 80 shown in accompanying drawing 3a--3c, form one at the top edge 801 of second concave inward structure and have drift angle and hypotenuse, protruding radial flange 81 to the cavity side, one guarantees drainage effect, two reduce top edge takies the oil back chamber space, preferably, the drift angle width L of this radial flange is 0.5mm～2mm; Angle of inclination beta is 20 °～40 °; Hypotenuse height h is 2mm～5mm, because the drift angle width is relatively short, as long as lubricant oil falls within on this drift angle, just can enter into groove by rapid hypotenuse along the inclination angle like this, and be guided to the fuel tank of bottom along the internal face of second concave inward structure 80, make the oil return process more smooth and easy.
Further, shown in accompanying drawing 3a--3c, for further making oil flow back into oil back chamber smoothly, the outer shroud edge of first disk, 18 bearing sides also can form one towards the oily structure 181 of getting rid of of first oil back chamber 100 to realize getting rid of oily effect, preferred this gets rid of oily structure 181 and stretched to first oil back chamber 1000 vertically by the outer shroud edge of first disk, 18 bearing sides, and form a disc 1811 that has a groove 1812 on inclined-plane 18121, like this because the rotor high-speed rotation, under centrifugal action, be attached to oil on the disc can be along the inclined-plane tangentially direction throw away, preferably, disc drift angle width L1:0.5～1.5mm; Get rid of oily angle γ: 10 °～30 °; Disc height h1:0.5～2mm; Inside grooves knuckle R:0.3～1.5mm.
Further, referring to accompanying drawing 1,2, it comprises that one is fixed on the baffle plate 10 on the described compressor box rear wall 52 and is fixed on the 3rd disk 9 that forms rotatable sealing on this baffle plate 10 with compressor drum rear disk 910, for further increasing the oil back chamber volume, preferably, shown in accompanying drawing 4a, Fig. 4 b, the 3rd disk 9 also adopts the indent form, and it is at the 3rd concave inward structure 90 that has water conservancy diversion inclined-plane 91 towards the front-end face formation one of first sliding bearing.
Further, as shown in Figure 5, also can be by baffle plate 10 across forming recessed the 4th concave inward structure 100 to baffle plate 10 at the 3rd disk 9 rear walls 52 and described casing rear wall 52, preferably, as shown in Figure 5, baffle plate 10 also forms an axial ledge 101 to the extension of clutch shaft bearing side vertically, this axial ledge radial compaction is realized the location in the upper end of rear wall 52, thereby make baffle plate and rear wall the upper end easier the assurance within size requirement of coaxality, and can not depart from size requirement because workman's misoperation causes baffle plate and the assembling of rear wall upper end, also improved efficiency of assembling and assembling difficulty simultaneously.The so ingenious setting of baffle plate not only can utilize flanged structure to realize the facility of positioning action and mounting process, with the synthetic concave inward structure of the 3rd disc set, is to achieve many things at one stroke also.
Further, shown in accompanying drawing 1,2, for further increasing the oil back chamber volume, the rear wall 52 that the antetheca 51 of compressor first casing forms the 5th concave inward structure 510 and/or described compressor first casing forms the 6th concave inward structure 520.
Further, shown in accompanying drawing 1,2, first drainback passage 53 that the bottom of first oil back chamber 3 removably is connected with on the diapire that first shrouding, 512, the first shroudings are provided with first through hole 5121 and described first casing is communicated with that oil return is discharged.Preferably, first shrouding is positioned at the bottommost of motor clutch shaft bearing oil back chamber, can take full advantage of the oil storage space that bottom half increases oil back chamber like this.
By foregoing description as seen, the setting of the above-mentioned concave inward structure of this embodiment of the utility model, utilized the installation environment of first sliding bearing farthest to realize the increase of the first oil back chamber volume of first sliding bearing cleverly, moreover, the utility model also utilizes the details of concave inward structure to make concave inward structure have good water conservancy diversion effect more simultaneously when utilizing the formation concave inward structure to increase the oil back chamber volume.These ingenious designs of suiting measures to local conditions all make the oil return apparatus that the utility model proposes increase the volume of oil back chamber greatly under the situation that does not increase rotor length and compressor overall volume, for the oil return of bearing provides good backflow environment, prior art has unforeseeable technique effect relatively.
Be the Security of raising straight connection type centrifugal compressor rotor and the stability of operation; compressor also is provided with second sliding bearing 2 at the afterbody of rotor usually; based on the similar model utility principle of above-mentioned model utility, at the environment that arranges of second bearing, the constituted mode of this oil return apparatus is:
As accompanying drawing 1, accompanying drawing 6a is to shown in the accompanying drawing 6c, second casing 6 that is formed on second sliding bearing, 2 bottoms has a cavity and forms second oil back chamber 2000, second casing 6 has antetheca 61 and rear wall 62 in the axial direction, also fixedly have on the antetheca 61 of second casing 6 and be sleeved on the 4th disk 13 that has seal action on the rotor shaft, back shrouding is also fixedly arranged on the rear wall 62 of second casing 6, the antetheca 61 of second casing 6, the 4th sealed disc 13 common antethecas 61 that constitute second oil back chamber 2000, the rear wall 62 of second casing 6, the common rear wall 62 that constitutes second oil back chamber 2000 of back shrouding, and the 4th sealed disc 13 forms the 7th axial concave inward structure 130 and/or back shrouding 14 forms the 8th axial concave inward structure 140 in second oil back chamber, 2000 sides in second oil back chamber, 2000 sides, makes second oil back chamber 2000 have the axial width that width W 2 are installed greater than second sliding bearing 2 in top at least therein.Equally, the utility model has the axial width that width is installed greater than second sliding bearing because concave inward structure guarantees the middle and upper part of second oil back chamber at least, not only increased the total measurement (volume) of oil back chamber, the lubricant oil that also makes centrifugal compressor throw away in rotating at a high speed can easier be discharged, and can enter in the bigger space at the very start release energy, speed reduces, thereby is beneficial to very fast the getting back in second refluxing chamber 2000 of oil.
Preferably, back shrouding 14 has a through hole 141, through hole outer end sealing liquid-sighting glass 15 is installed, be combined together the 8th concave inward structure 140 that forms on the back shrouding by through hole and liquid-sighting glass 15.So, the through hole on the back shrouding 14 has not only increased the volume of oil back chamber, also be convenient to by liquid-sighting glass 15 clear liquid level and oil return situations of checking oil back chamber, and be to achieve many things at one stroke.
Preferably, for further increasing the oil back chamber volume, above second oil back chamber 2000, also be provided with upper cover plate 7, the upper end of one end and the 4th disk 13 is installed together, the other end is installed together with the upper end of back shrouding 14, preferably, upper cover plate 7 forms a radial flange 71 to the extension of second oil back chamber, 2000 sides, this radial flange is sleeved on the outside of second sliding bearing 2 and forms the indent end face relative with the 4th disk 13, this end face produces the 9th concave inward structure 70, further preferred, upper cover plate 7 forms the tenth concave inward structure 700 on the end face of second oil back chamber 2000.
Further, for oil can be refluxed smoothly, the antetheca 61 of second casing 6 forms downward plane of inclination and is back to the bottom of second oil back chamber smoothly better to make oil, preferably, form the oil return step of inclination between antetheca and the 4th sealed disc, for making oil return more smooth and easy, tilt angle alpha should be greater than 45 °.
Preferably, for the fastening piece that guarantees back shrouding and the second casing rear wall has enough scyewed joint degree of depth, the rear wall 62 of the utility model second casing forms the oil return scalariforms, certainly also can be further between back shrouding 14 and rear wall 62 formation oil return step with the volume of further increase oil back chamber with satisfy the needs that the liquid-sighting glass fastener threads connects the degree of depth.
Further, be to improve the water conservancy diversion effect of oil return, so that lubricant oil is back to oil back chamber smoothly along the inner concave of concave inward structure, the interior ring edge of the 4th disk 13 forms a radial flange 131 with drift angle and hypotenuse, preferably, the width L of this radial flange drift angle is 0.5mm～2mm; Angle of inclination beta is 20 °～40 °; Hypotenuse height h is 2mm～5mm, because the drift angle width of radial flange is shorter, as long as lubricant oil falls within on this drift angle, just can enter into groove by rapid hypotenuse along the inclination angle like this, and the groove on circumference be guided to the bottom fuel tank, make the oil return process more smooth and easy.
For the oil that makes second oil back chamber causes first oil back chamber or independently draws back external fuel tank, second casing 6 is formed with drainback passage 41 in the bottom of second oil back chamber 2000, the bore of this drainback passage is less than the area of section of oil back chamber, in order to dock better with foregoing first pipeline or second pipeline.
In the formation structure of above-mentioned second oil back chamber, the antetheca 61 of second casing and the 4th disk 13 have constituted the oil back chamber part on the second bearing left side, back shrouding 14, upper cover plate 7, liquid-sighting glass 15 have constituted the oil back chamber part on second bearing the right, have constituted second oil back chamber 2000 jointly by left and right sides two-part oil back chamber.
This embodiment of the application is by the setting of above-mentioned concave inward structure, also utilized the installation environment of second sliding bearing cleverly, make the second oil back chamber volume of second sliding bearing increase greatly, moreover, the application also utilizes the detailed design of concave inward structure to make concave inward structure have better water conservancy diversion effect when utilizing the formation concave inward structure to increase the oil back chamber volume.These ingenious designs of suiting measures to local conditions all make the oil return structure that the application proposes can the maximum using installation environment, and prior art has unforeseeable technique effect relatively.
Above-mentioned two kinds of oil return apparatus can exist in the centrifugal compressor simultaneously, also can the individualism centrifugal compressor in.
First, second bearing is installed simultaneously and is had above-mentionedly during at the set oil return apparatus of clutch shaft bearing, second bearing when compressor, the oil return of two oil back chambers can adopt following mode to draw the oil sump tank (not shown):
One of method, as shown in Figure 1, the oil returns in second oil back chamber 2000 cause in first oil back chamber 1000 by first pipeline 341, and first oil back chamber by motor first sliding bearing draws oil and is back to fuel tank then.So the volume of the best first casing cavity 50 is more than or equal to first sliding bearing 1 and first sliding bearing, 2 dredge oil amount sums, so that the lubricant oil volume of two bearing releases is less than the oil back chamber volume, lubricant oil releases energy in bigger space like this, speed reduces, be conducive to the very fast fuel tank that is back to of oil, and be preferably on the level height, the end that first pipeline 341 links to each other with second casing 6 is equal to or higher than the end that first pipeline links to each other with first casing, can reduce flow resistance like this, maybe when being higher than first pipeline with end that first casing links to each other, can utilize the gravity effect to accelerate lubricant oil and be back to first oil back chamber, increase the oil return effect.
Two of method, as shown in Figure 7, the oil return in first oil back chamber 3 causes in second oil back chamber by second pipeline 342, by second oil back chamber under motor second sliding bearing oil is drawn then to be back to fuel tank.Thus, the volume of second oil back chamber 2000 is more preferably greater than equaling first sliding bearing 1 and first sliding bearing, 2 dredge oil amount sums, and is preferably in the end that second pipeline links to each other with first casing on the level height and is equal to or higher than the end that second pipeline links to each other with second casing 6.
Three of method, as shown in Figure 8, the oil returns in the oil return in the first casing cavity 50 or the second casing cavity 60 are all directly drawn by pipeline and are back to fuel tank.At this moment, two oil back chambers can suitably reduce.
Above-mentioned three kinds of methods are tackled the certain nargin coefficient of oil back chamber volume consideration separately in the flow resistance of considering that oily oneself viscosity brings.But it is relatively comprehensive, preferred the third mode of the utility model, can make first oil back chamber and second oil back chamber do smallerly like this, reduce cost, in addition, owing to there is not the connection of first pipeline and second pipeline, can save the expanded joint manufacturing procedure, can reduce the flow resistance of lubricant oil in pipeline, simultaneously, front and back oil return process is not disturbed mutually yet.For above-mentioned first pipeline and second pipeline, the two ends of the two ends of first pipeline 341 or second pipeline 342 can be by the be tightly connected two ends flanged surface of motor cylindrical shell 16 of expanded joint mode or welding manner; Perhaps, first pipeline 341 or second pipeline 342 are cast into one with motor cylindrical shell 16.
Above-mentioned design of the present utility model, be applicable to one or more levels impeller especially multi-stage impeller be arranged on the situation (as shown in Figure 1) of the cantilever end of rotor in the same way in turn, and its rotor speed can be more than 6000 rev/mins, even more than 7000 rev/mins, its motor can be the DC frequency-changing synchronous machine, especially the DC frequency-changing synchronous machine of power between 150kW to 800kW.The application can both reach good effect.
The front has been done comprehensive description by specific embodiments at the utility model, below the technique effect that can bring the utility model be summarized as follows:
1, the high speed characteristics of the utility model straight connection type centrifugal compressor and the work characteristics of sliding bearing, we will guarantee at least that the middle and upper part of oil back chamber has the axial width that width is installed greater than first sliding bearing by the special concave inward structure that proposes, and prior art is not also recognized this point before.Such design has not only increased the total measurement (volume) of oil back chamber, the lubricant oil that also makes centrifugal compressor throw away in rotating is at a high speed not only discharged easily, can also enter in the bigger space quickly and release energy, underspeed, thereby be beneficial to landing and the backflow of oil.
2, require can not long, compact structure characteristics for the centrifugal compressor rotor that also further drives at the motor direct connection of the utility model, under the situation that does not influence original component function, maximum utilize the set environment of bearing to form multiple concave inward structure to increase the oil back chamber volume, this kind improvement, compare only by increasing the prior art that tank-volumes increases the refluxing chamber volume, though sacrificed the thickness as the parts of oil back chamber front and rear wall to a certain extent, General strengthens greatly.
3, the utility model is when considering concave inward structure, some parts that form concave inward structure have further been carried out the ingenious design of other functions as first shrouding, back shrouding, baffle plate, first disk, second disk, the 3rd disk, the 4th disk and even first, second casing front and rear wall, make it when increasing the backflow space, also obtain other effects of achieving many things at one stroke.
4, above-mentioned design is neither causing rotor length to increase, do not cause the compressor box volume or weight to increase yet, also do not cause under the prerequisite of weakening of other functions of parts that are mated, make the high temperature grease that comes out from bearing can flow to oil back chamber rapidly and drain into fuel tank, make the oil back chamber oil level can not be dipped in the seal interface and avoided the leakage of lubricant oil in the seal interface, the Security of rotor and bearing improves greatly.
Explanation is at last:
Although describe and illustrate various creative aspect of the present utility model, concept and feature in this article, implement them in the exemplary embodiment by combination, but can in many alternate embodiments, use aspect different embodiments various, concept and feature, individually or in the mode of various combinations and sub-portfolio thereof.Unless be explicitly excluded in this article outside, the combination that all are such and sub-portfolio intention all are in scope of the present utility model.
In addition, although may describe the various preferred implementations about various aspects of the present utility model, concept and feature in this article, but these descriptions are not the complete or detailed inventories of all mode of executions of the utility model, these descriptions do not show that these features are essential, exclusiveness.The description of the application's illustrative methods or structure is not limited to comprise desired all features in all cases, unless clearly be set fourth as this situation.
Claims (50)
1. oil return apparatus that is used for the straight connection type centrifugal compressor, this compressor has first sliding bearing that is installed between motor rotor core and the impeller, it is characterized in that: it makes compressor first casing that is positioned at this first sliding bearing bottom have a cavity and forms first oil back chamber, first casing has antetheca and rear wall at axial direction, the upper end of this antetheca is provided with preceding disk, should before disk be installed in the rotating shaft between impeller and first sliding bearing, have the sealing effect of isolation impeller and first sliding bearing; The upper end of rear wall is provided with rear disk, and this rear disk is installed in the rotating shaft between first sliding bearing and the electric machine iron core, has the sealing effect of isolating first sliding bearing and electric machine iron core; The common antetheca that constitutes described first oil back chamber of the antetheca of disk and described first casing before described, the rear wall of described rear disk and described first casing is common constitute described first oil back chamber rear wall and described before or after disk forming axial concave inward structure towards the first oil back chamber side, make described first oil back chamber have the axial width that width is installed greater than first sliding bearing at least in the middle and upper part of its first oil back chamber.
2. the oil return apparatus for the straight connection type centrifugal compressor according to claim 1, it is characterized in that: disk is a complex disc before described, it comprises that one is fixed on the compressor drum and is fixed on the described compressor first casing antetheca not with axle with first disk and that rotor rotates and rotates, is positioned at second disk that the first disk periphery and described antetheca are set together, and two disks are combined together has the oil of isolating between compressor refrigerant lateral lobe wheel and the tank side bearing, the seal action of gas leakage.
3. the oil return apparatus for the straight connection type centrifugal compressor according to claim 2 is characterized in that: first disk forms first concave inward structure and/or described second disk to the hole enlargement of bearing side at the ear end face of its bearing side and forms second concave inward structure at the ear end face of its bearing side.
4. the oil return apparatus for the straight connection type centrifugal compressor according to claim 3 is characterized in that: described second disk forms a radial flange with drift angle and hypotenuse at the top edge of second concave inward structure; And/or the outer shroud edge of the described first disk bearing side forms one towards the oily structure of getting rid of of first oil back chamber.
5. the oil return apparatus for the straight connection type centrifugal compressor according to claim 4, it is characterized in that: the drift angle width L of described radial flange is 0.5mm～2mm; Angle of inclination beta is 20 °～40 °; Hypotenuse height h is 2mm～5mm.
6. the oil return apparatus for the straight connection type centrifugal compressor according to claim 4 is characterized in that: describedly get rid of oily structure and stretched to first oil back chamber vertically by the outer shroud edge of the first disk bearing side, and form a disc that has a groove on inclined-plane.
7. the oil return apparatus for the straight connection type centrifugal compressor according to claim 6 is characterized in that: disc drift angle width L1:0.5～1.5mm; Get rid of oily angle γ: 10 °～30 °; Disc height h1:0.5～2mm; Inside grooves knuckle R:0.3～1.5mm.
8. require each described oil return apparatus for the straight connection type centrifugal compressor according to aforesaid right, it is characterized in that: described rear disk comprises that one is fixed on the baffle plate on the described compressor box rear wall and is fixed on the 3rd disk that forms rotatable sealing on this baffle plate with compressor drum.
9. the oil return apparatus for the straight connection type centrifugal compressor according to claim 8 is characterized in that: the 3rd disk forms one at the front-end face of described bearing and has the 3rd concave inward structure on water conservancy diversion inclined-plane and/or described baffle plate by across forming recessed the 4th concave inward structure to baffle plate at the 3rd disk rear wall and described casing rear wall.
10. the oil return apparatus for the straight connection type centrifugal compressor according to claim 9 is characterized in that: described baffle plate also forms an axial ledge of extending to the clutch shaft bearing side vertically, and this axial ledge radial compaction is in the upper end of described rear wall.
11. require each described oil return apparatus for the straight connection type centrifugal compressor of 1-7 according to aforesaid right, it is characterized in that: the rear wall that the antetheca of described compressor first casing forms the 5th concave inward structure and/or described compressor first casing forms the 6th concave inward structure.
12. require 8 described oil return apparatus for the straight connection type centrifugal compressor according to aforesaid right, it is characterized in that: the rear wall that the antetheca of described compressor first casing forms the 5th concave inward structure and/or described compressor first casing forms the 6th concave inward structure.
13. require 9 described oil return apparatus for the straight connection type centrifugal compressor according to aforesaid right, it is characterized in that: the rear wall that the antetheca of described compressor first casing forms the 5th concave inward structure and/or described compressor first casing forms the 6th concave inward structure.
14. require each described oil return apparatus for the straight connection type centrifugal compressor of 1-7 according to aforesaid right, it is characterized in that: the bottom of first oil back chamber removably is connected with first shrouding, and the drainback passage that first shrouding is provided with on the diapire of first through hole and described first casing is communicated with that oil return is discharged.
15. require 8 described oil return apparatus for the straight connection type centrifugal compressor according to aforesaid right, it is characterized in that: the bottom of first oil back chamber removably is connected with first shrouding, and the drainback passage that first shrouding is provided with on the diapire of first through hole and described first casing is communicated with that oil return is discharged.
16. require 11 described oil return apparatus for the straight connection type centrifugal compressor according to aforesaid right, it is characterized in that: the bottom of first oil back chamber removably is connected with first shrouding, and the drainback passage that first shrouding is provided with on the diapire of first through hole and described first casing is communicated with that oil return is discharged.
17. require 12 described oil return apparatus for the straight connection type centrifugal compressor according to aforesaid right, it is characterized in that: the bottom of first oil back chamber removably is connected with first shrouding, and the drainback passage that first shrouding is provided with on the diapire of first through hole and described first casing is communicated with that oil return is discharged.
18. oil return apparatus that is used for the straight connection type centrifugal compressor, the afterbody of its rotor is provided with second sliding bearing, second casing that is formed on second sliding bearing bottom has a cavity and forms second oil back chamber, described second casing has antetheca and rear wall in the axial direction, fixedly have on the antetheca of second casing and be sleeved on the 4th disk that has seal action on the rotor shaft, back shrouding is also fixedly arranged on the rear wall of second casing, it is characterized in that: the antetheca of described second casing, the common antetheca that constitutes second oil back chamber of the 4th sealed disc, the rear wall of described second casing, the common rear wall that constitutes second oil back chamber of back shrouding, and described the 4th sealed disc forms the 7th axial concave inward structure and/or the back shrouding forms the 8th axial concave inward structure in the second oil back chamber side in the second oil back chamber side, makes described second oil back chamber have the axial width that width is installed greater than second sliding bearing in top at least therein.
19. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 18 is characterized in that: the interior ring edge formation one of described the 4th disk has the radial flange of drift angle and hypotenuse.
20. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 19 is characterized in that: this radial flange drift angle width L is 0.5mm～2mm; Angle of inclination beta is 20 °～40 °; Hypotenuse height h is 2mm～5mm.
21. as claim 19 or 20 described oil return apparatus for the straight connection type centrifugal compressor, it is characterized in that: the antetheca of described second casing forms downward plane of inclination, the angle of inclination of described plane of inclination is α, 75 ° 〉=α 〉=15 °.
22. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 21 is characterized in that: the angle of inclination of described plane of inclination is 60 ° 〉=α 〉=30 °.
23. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 21, it is characterized in that: above described second casing, also be provided with upper cover plate, the upper end of one end and the 4th disk is installed together, the upper end of the other end and described back shrouding is installed together, described upper cover plate forms a radial flange to the extension of the second oil back chamber side, this radial flange is sleeved on the outside of second sliding bearing, and itself and the 4th disk opposing end faces produce the 9th concave inward structure towards second oil back chamber, and described upper cover plate also forms the tenth concave inward structure towards the end face of second oil back chamber.
24. as each described oil return apparatus for the straight connection type centrifugal compressor of claim 18-20, it is characterized in that: described back shrouding forms a through hole, through hole outer end sealing liquid-sighting glass is installed, be combined together by through hole and liquid-sighting glass and form described the 8th concave inward structure.
25. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 21, it is characterized in that: described back shrouding forms a through hole, through hole outer end sealing liquid-sighting glass is installed, be combined together by through hole and liquid-sighting glass and form described the 8th concave inward structure.
26. as each described oil return apparatus for the straight connection type centrifugal compressor of claim 18-20, it is characterized in that: wall forms stairstepping before or after described second casing.
27. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 21 is characterized in that: wall forms stairstepping before or after described second casing.
28. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 23 is characterized in that: wall forms stairstepping before or after described second casing.
29. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 24 is characterized in that: wall forms stairstepping before or after described second casing.
30. as each described oil return apparatus for the straight connection type centrifugal compressor of claim 18-20, it is characterized in that: described second casing is formed with drainback passage in the bottom of second oil back chamber, and the bore of this drainback passage is less than the area of section of oil back chamber.
31. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 21 is characterized in that: described second casing is formed with drainback passage in the bottom of second oil back chamber, and the bore of this drainback passage is less than the area of section of oil back chamber.
32. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 23 is characterized in that: described second casing is formed with drainback passage in the bottom of second oil back chamber, and the bore of this drainback passage is less than the area of section of oil back chamber.
33. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 24 is characterized in that: described second casing is formed with drainback passage in the bottom of second oil back chamber, and the bore of this drainback passage is less than the area of section of oil back chamber.
34. the oil return apparatus for the straight connection type centrifugal compressor as claimed in claim 26 is characterized in that: described second casing is formed with drainback passage in the bottom of second oil back chamber, and the bore of this drainback passage is less than the area of section of oil back chamber.
35. as each described oil return apparatus of claim 1-7,18-20, it is characterized in that: the rotating speed of its rotor is more than 6000 rev/mins.
36. oil return apparatus as claimed in claim 35 is characterized in that: the rotating speed of its rotor is more than 7000 rev/mins.
37. oil return apparatus as claimed in claim 35 is characterized in that: described motor is the DC frequency-changing synchronous machine, and its power is between 150kW to 800kW.
38. oil return apparatus as claimed in claim 35, its feature exists: described sliding bearing is hydraulic bearing.
39. oil return apparatus as claimed in claim 38, its feature exists: between the inner cylindrical surface of described hydraulic bearing and the rotor journal external cylindrical surface, the axial end of bearing and bearing is carried out all be formed with the oil groove that can produce the oil film kinetic pressure between the rotor radial flange end face of axially locating.
40. a straight connection type centrifugal compressor, it has each described oil return apparatus of claim 1-17 and/or each described oil return apparatus of claim 18-34.
41. straight connection type centrifugal compressor as claimed in claim 40, it is characterized in that: when it has each described oil return apparatus of claim 1-6 and each described oil return apparatus of claim 7-13 simultaneously, oil return in described second oil back chamber causes in first oil back chamber by first pipeline, and the volume of the first casing cavity is more than or equal to first sliding bearing and the second sliding bearing dredge oil amount sum.
42. straight connection type centrifugal compressor as claimed in claim 41 is characterized in that: on level height, the end that described first pipeline links to each other with second casing is equal to or higher than the end that first pipeline links to each other with first casing; Perhaps, the oil return in first oil back chamber causes in second oil back chamber by second pipeline, and the volume of second oil back chamber is more than or equal to first sliding bearing and the second sliding bearing dredge oil amount sum.
43. straight connection type centrifugal compressor as claimed in claim 42 is characterized in that: on level height, the end that second pipeline links to each other with first casing is equal to or higher than the end that second pipeline links to each other with second casing; Perhaps, the oil return in the first casing cavity or the oil return in the second casing cavity are all directly drawn by pipeline and are back to fuel tank.
44. according to each described straight connection type centrifugal compressor of claim 41-43, it is characterized in that: described compressor is one or more levels impeller.
45. according to the described straight connection type centrifugal compressor of claim 44, it is characterized in that: described multi-stage impeller is arranged on the cantilever end of rotor in the same way in turn.
46. as each described straight connection type centrifugal compressor of claim 40-43, it is characterized in that: the rotating speed of its rotor is more than 6000 rev/mins.
47. straight connection type centrifugal compressor as claimed in claim 46 is characterized in that: the rotating speed of its rotor is more than 7000 rev/mins.
48. straight connection type centrifugal compressor as claimed in claim 46 is characterized in that: described motor is the DC frequency-changing synchronous machine, and its power is between 150kW to 800kW.
49. as each described straight connection type centrifugal compressor of claim 40-43, its feature exists: described sliding bearing is hydraulic bearing.
50. straight connection type centrifugal compressor as claimed in claim 49, its feature exists: between the inner cylindrical surface of described hydraulic bearing and the rotor journal external cylindrical surface, the axial end of bearing and bearing is carried out all be formed with the oil groove that can produce the oil film kinetic pressure between the rotor radial flange end face of axially locating.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220151388 CN203146401U (en) | 2012-04-02 | 2012-04-02 | Direct-connected radial compressor and oil return apparatus thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220151388 CN203146401U (en) | 2012-04-02 | 2012-04-02 | Direct-connected radial compressor and oil return apparatus thereof |
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| Publication Number | Publication Date |
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| CN203146401U true CN203146401U (en) | 2013-08-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201220151388 Expired - Lifetime CN203146401U (en) | 2012-04-02 | 2012-04-02 | Direct-connected radial compressor and oil return apparatus thereof |
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| CN (1) | CN203146401U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103362853A (en) * | 2012-04-02 | 2013-10-23 | 珠海格力电器股份有限公司 | Direct-connection centrifugal compressor and oil-return device thereof |
| CN105114341A (en) * | 2015-09-01 | 2015-12-02 | 广东美芝制冷设备有限公司 | Centrifugal compressor and room air conditioner comprising same |
-
2012
- 2012-04-02 CN CN 201220151388 patent/CN203146401U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103362853A (en) * | 2012-04-02 | 2013-10-23 | 珠海格力电器股份有限公司 | Direct-connection centrifugal compressor and oil-return device thereof |
| CN105114352A (en) * | 2012-04-02 | 2015-12-02 | 珠海格力电器股份有限公司 | Direct-connected radial compressor and oil return device thereof |
| CN105114352B (en) * | 2012-04-02 | 2018-03-13 | 珠海格力电器股份有限公司 | A kind of oil return apparatus for direct-connection centrifugal compressor |
| CN105114341A (en) * | 2015-09-01 | 2015-12-02 | 广东美芝制冷设备有限公司 | Centrifugal compressor and room air conditioner comprising same |
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Granted publication date: 20130821 |