CN203081853U - High-speed fluid power machine - Google Patents
High-speed fluid power machine Download PDFInfo
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- CN203081853U CN203081853U CN 201220151354 CN201220151354U CN203081853U CN 203081853 U CN203081853 U CN 203081853U CN 201220151354 CN201220151354 CN 201220151354 CN 201220151354 U CN201220151354 U CN 201220151354U CN 203081853 U CN203081853 U CN 203081853U
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- dynamic power
- fluid dynamic
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Abstract
The utility model relates to a high-speed fluid power machine with rotation speed above 6000rpm, and particularly between 7000rpm and 20000rpm. The high-speed fluid power machine comprises a driving motor and a rotor. The rotor comprises a driving motor rotating shaft and a rotating impeller which applies work on fluid. The rotating impeller is directly equipped on a rotating shaft of the driving motor. Furthermore a no-key connection mode is adopted for the rotating impeller. In a radial direction, the rotating impeller is in interference positioning with the driving motor through a hot pressing mode; and in an axial direction, the rotating impeller is compressed and abuts against a radial flange of the rotating shaft by a locking structure. According to the high-speed fluid power machine, through directly equipped the rotating impeller on the rotating shaft of the driving motor, the transmission efficiency is greatly improved. Simultaneously the high-speed fluid power machine has the following advantages: relatively simple rotor detachment process, high coaxiality between the impeller and the rotating shaft, high sealing performance, small vibration, etc.
Description
Technical field
The utility model relates to a kind of rotor of high-velocity fluid dynamic power machine, and especially a kind of rotating speed is at the rotor of the high-velocity fluid dynamic power machine more than the 6000rpm (as the high rotating speed centrifugal compressor of rotating speed more than 10000rpm).
Background technique
Present high-velocity fluid dynamic power machine is the high speed centrifugation compressor of field of air conditioning especially, mostly by overdrive gear rotating speed is brought up to design speed, and the impeller rotation is to the acting of incoming flow gas, thus the raising gas pressure.The compressor arrangement of this routine has the following disadvantages: (1) has increased the mechanical loss of compressor owing to have the intermediate gear speedup box, thereby increases the compressor power consumption, influences unit performance; (2) existence of gear-box increases the form structure of compressor greatly, makes casing seem huge, heavy, and cost also increases thereupon; (3) because the rotating speed of centrifugal compressor is very high, and gear up process noise is very big, therefore the noise of conventional centrifuge is commonly about 93 decibels, makes it need additionally to increase soundproof measures in engineering is used, and causes engineering cost to increase; (4) the used motor of conventional centrifugal compressor is a threephase asynchronous machine, and electric efficiency is up to about 94%, if want further to improve efficiency on motor, difficulty is very big; (5) frequency conversion of conventional centrifugal compressor belongs to slow-speed of revolution frequency conversion category, that is: on common threephase asynchronous machine, increase the frequency variator mode, though this mode can improve part load performance with respect to fixed mode frequently, but because the existence of gear drive, bring the mechanical transmission loss, apparent in view when sub load especially, so the part load performance room for promotion also is restricted.
For this reason, the utility model proposes impeller directly is assemblied on the motor shaft,, but can bring following problem thus with the problems referred to above of avoiding the intermediate gear speedup box to be brought:
1, because the part of motor shaft need be installed impeller, therefore cause the cantilever segment of motor shaft long, make the natural bow that is produced by deadweight increase, the rigidity of axle is affected;
2, directly drive by the high-speed electric expreess locomotive axle owing to impeller, the installation requirement of impeller and motor shaft improves greatly, therefore select what kind of processing, mounting type just can make impeller and rotor keep high concentricity and running accuracy and high intensity in the high speed rotating process, it is extremely important that vibration and phenomenon of rupture do not take place;
3, under high rotating speed, how to guarantee that installation between impeller and the rotating shaft can reach simultaneously higher sealing effect to avoid impeller loss and interstage losses also very important.
And mostly realize being connected by key with rotating shaft in view of the easy accessibility impeller in the prior art, the machined surface quality of key junction surface is had relatively high expectations, simultaneously, discontinuity during work, occurring stress easily concentrates, we find by experiment, especially the high-velocity fluid dynamic power machine of rotating speed more than 10000rpm, advocate to concentrate on key root and keyway root, the impeller bearing capacity is reduced, very easily fatigue failure of impeller when causing work, the load that can not withstand shocks, and key often occurs and pressed erosion, fracture, keyway is out of shape and rolls the key phenomenon, occurs producing between impeller and the rotating shaft eccentric thus, increase situations such as additional energy imbalance, have a strong impact on the service behaviour of high-velocity fluid dynamic power machine, this phenomenon especially rotating speed seems even more serious on the high-speed centrifugal compressor more than the 10000rpm.
By above-mentioned prior art as can be seen, how to provide a kind of and can realize that efficient transmission can realize that again safe rotor is the technical problem that related domain needs to be resolved hurrily.
The model utility content
In view of the above-mentioned problems in the prior art, main purpose of the present utility model is to address the deficiencies of the prior art, provide a kind of rotating speed more than 6000rpm, especially the high-velocity fluid dynamic power machine of rotating speed between 7000rpm～20000rpm, it comprises drive motor and rotor, rotor comprises the rotary blade of drive motor rotating shaft and convection cell acting, it is characterized in that: described rotary blade is directly installed in the rotating shaft of drive motor, and described rotary blade adopts no key Placement, be positioned at drive motor rotating shaft interference by hot pressing mode diametrically, the structure that is locked on axially compresses and leans on a radial flange of rotating shaft.
Further, described rotary blade is a multi-stage impeller, between this multi-stage impeller, be provided with positioning adapter, this positioning adapter is fixed in the rotating shaft of described motor by the interference orientation type on the one hand, forms between the impeller hub that its front and rear end is adjacent on the other hand and can transmit the second transmission of torque face that holds out against moment.
Further, described multi-stage impeller between the one-level impeller of front end and described locking mechanism, be formed with the first transmission of torque face, described multi-stage impeller between the impeller of rear end and described rotating shaft and radial flange thereof, be formed with the 3rd transmission of torque face.
Further, the described first and/or second transmission of torque face and/or the 3rd transmission of torque mask have certain gradient, and be preferred, and the described gradient is spent between 25 degree 7; And/or described first and/or second transmission of torque face and/or the 3rd transmission of torque mask the convex-concave cooperating structure that increases the friction force effect is arranged.
Further, the front-end face of described positioning adapter forms first axial ledge, and the inner peripheral surface of the wheel hub of the impeller that is adjacent is realized compression fit radially; Further preferred, the compression fit between the wheel hub of the impeller that described first axial ledge is adjacent is an interference fit; Further preferred, the ear end face of described positioning adapter forms second axial ledge, and the inner peripheral surface of the wheel hub of the impeller that this second axial ledge is adjacent is a Spielpassung; Further preferred, the outer peripheral surface of described positioning adapter is formed with to be beneficial to and improves fluid and enter the arc transition section that flows of impeller thereafter, tangent connection between the wheel hub of the impeller that this arc transition section is adjacent.
Further, described locking mechanism is to be arranged on the epitrochanterian distolateral locking nut of one-level impeller eye that is positioned at, and applies with the location axle sleeve to described multi-stage impeller by this locking nut and holds out against moment; Preferably, the outer surface of described locking nut air flow inlet side has and the suitable streamline shape of air-flow airintake direction, preferably, the outer peripheral surface of described locking nut is formed with and is beneficial to the arc transition section that fluid enters the acting of one-level impeller, tangent connection between the wheel hub of the one-level impeller that this arc transition section is adjacent; Further preferred, the outer surface of described locking nut air flow inlet side is an arc surface; Further preferred, the front end of the outer surface of described locking nut air flow inlet side forms water conservancy diversion rib or the guiding gutter with certain guide functions.
Further, also be provided with the locating washer of increase power area of contact between described locking nut and the one-level impeller; Preferably, described locating washer is formed with axial slotting face and the transmission of torque face radially stretched, the described axial slotting inner peripheral surface of stretching the wheel hub of face and one-level impeller is combined together, described transmission of torque face one side radially acts on the ear end face of one-level impeller, opposite side acts on described locking nut and accepts and transmit the moment that holds out against that described locking nut applies, and forms the described first transmission of torque face between described locating washer and the one-level impeller.
Further, described each transmission of torque face utilizes the frictional force transmission between the acting surface, and friction factor is between 0.10～0.35, and preferred, far away more from locking nut, transmission of torque face friction factor is big more; Preferably, described multi-stage impeller adopts aluminum alloy, and forged steel is adopted in described rotating shaft, and friction factor is 0.25.
Further, between described impeller and the rotating shaft, between impeller and the positioning adapter, the interference location amount of interference fit is 0.01～0.02mm between positioning adapter and the rotating shaft, the required gap of assembling, heating back is chosen by the H7/g6 of fit diameter, wherein the upper deviation of diameter is closed in the H7 assignment, the lower deviation of diameter is closed in the g6 assignment, and the interference fit diameter A between described impeller and positioning adapter, impeller and rotating shaft is all roughly between 30～60mm.
Further, described impeller is a both stage impellers or greater than 2 grades multi-stage impeller, preferably this multi-stage impeller series aiding connection is installed in an end of drive motor rotating shaft.
Further, described high-velocity fluid dynamic power machine is the high-speed centrifugal compressor.
Further, described rotary blade is a multi-stage impeller, described locking mechanism is installed in the one-level impeller front end of multi-stage impeller, be provided with positioning adapter between the multi-stage impeller, all form between impeller and the locking mechanism, between this positioning adapter impeller adjacent and can transmit the transmission of torque face that holds out against moment with its left and right sides, make described multi-stage impeller under the effect that holds out against moment that locking mechanism applies, to be pressed in vertically on the radial flange of described rotating shaft by the transmission of torque face, preferably, described locking mechanism is a locking nut.
Further, described impeller, positioning adapter adopt aluminum alloy, and forged steel is adopted in rotating shaft.
Further, described high-velocity fluid dynamic power machine is the high-speed centrifugal compressor, and is preferred, and described high-speed centrifugal compressor is the straight connection type that impeller and drive motor rotating shaft are directly installed, described drive motor rotating shaft is a cantilever type, and described impeller is installed in the cantilever end of drive motor rotating shaft.
The utility model is by being directly installed on rotary blade in the rotating shaft of drive motor, improved transmission efficiency greatly, and because no key connects, rotary blade is positioned at drive motor rotating shaft interference by hot pressing mode diametrically, the structure that is locked axially compresses and leans on the radial flange of rotating shaft, avoided since key be arranged so that rotor stressed key root and the keyway root of mainly concentrating on, the impeller bearing capacity is reduced, very easily fatigue failure of impeller during work, load can not withstand shocks, key takes place pressed erosion, fracture, keyway distortion and roll the key phenomenon, produce eccentric between impeller and the rotating shaft, uneven, the generation of phenomenons such as vibration, also make rotor unloading process of the present utility model simple relatively simultaneously, the coaxality of impeller and rotating shaft is good, good airproof performance, vibrate little etc., also greatly reduce simultaneously owing to rotary blade is directly installed in the rotating shaft of drive motor and causes the long rotating shaft that makes that brings of cantilever segment of motor shaft to increase the negative influence of bringing for the rigidity of axle by the natural bow that deadweight produces.
First and/or the second transmission of torque face and/or the 3rd transmission of torque mask have the convex-concave cooperating structure that increases the friction force effect, so not only can make the efficient of transmission of torque higher, also can make to have each other between the moment transfer surface better to compress effect.
The utility model makes lining not only have the function of axially locating to taking all factors into consideration of lining, also has the guiding fluid and enters effect in the impeller that is adjacent with as far as possible little loss, has brought unforeseeable technique effect.
The utility model makes locking nut not only have conventional locking function to taking all factors into consideration of locking nut also to have the guiding fluid and enter effect in the impeller with as far as possible little loss, brought unforeseeable technique effect.
Description of drawings
Fig. 1 is the embodiment's of the utility model rotor a structural representation.
Fig. 2 a is the inlet stream effect schematic representation after the improvement of fastening nut of the utility model rotor.
Fig. 2 b is the preceding inlet stream effect schematic representation of improvement of the fastening nut of the utility model rotor.
Fig. 3 is the locking nut embodiment's of the utility model employing schematic representation.
The pairing component names of reference character in the accompanying drawing is:
Motor 1,
The second transmission of torque face 304 between positioning adapter and the impeller;
The 3rd transmission of torque face 302 between the radial flange of impeller and axle;
The axial ledge 41,42 of positioning adapter;
Spielpassung face 321 between one-level impeller and the locating washer;
The slotting face 51 of stretching of locating washer;
The first transmission of torque face 52 between one-level impeller and the locking mechanism;
The water conservancy diversion rib 61 of locking nut.
Embodiment
At first need to prove, the front end of the parts described in the utility model, front side, front, rear end, rear side, back are distinguished according to the air current flow direction, as shown in Figure 1, the airintake direction of setting air-flow is front end or front side or front, and the outflow direction of setting air-flow is rear end, rear side, back.
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.
Embodiment below in conjunction with accompanying drawing 1-3 explanation the application high-velocity fluid dynamic power machine required for protection:
Advantage of the present utility model is to be suitable for the high-velocity fluid dynamic power machine, especially rotating speed is more than 6000rpm, as the high-speed centrifugal compressor of rotating speed between 7000rpm～20000rpm, it is preferred embodiment that present embodiment adopts the high-speed centrifugal compressor of R134a working medium with working medium, and this working medium can better adapt to this operating range of the centrifugal compressor that freezes under this kind rotating speed.The high-velocity fluid dynamic power machine of rotating speed will consider to have very high transmission efficiency on the one hand like this, to consider also that on the other hand the impeller 3 and the installation of rotating shaft 2 have very high soundness and Security, especially to guarantee that impeller 3 and rotating shaft 2 keep higher coaxality in the high speed rotating process, also needing simultaneously to consider can be convenient for assembly, has lower technology cost, take all factors into consideration those factors, our special proposition is suitable for the following structure of above-mentioned high-velocity fluid dynamic power machine:
It comprises drive motor and rotor 2345, rotor 2345 comprises the rotary blade 3 of drive motor rotating shaft 2 and convection cell acting, it is characterized in that: described rotary blade 3 is directly installed in the rotating shaft 2 of drive motor, and described rotary blade 3 is positioned at drive motor rotating shaft 2 interference by hot pressing mode diametrically, and the structure that is locked on axially compresses and leans on a radial flange 21 of rotating shaft 2.
Embodiment as shown in Figure 1, the Spielpassung face 321 between one-level impeller and the locating washer, the interference locating face 322 between sencond stage impeller and the rotating shaft.
The utility model is by being directly installed on rotary blade 3 in the rotating shaft 2 of drive motor, improved transmission efficiency greatly, and because no key connects, rotary blade 3 is positioned at drive motor rotating shaft 2 interference by hot pressing mode diametrically, the structure that is locked axially compresses and leans on the radial flange 21 of rotating shaft 2, avoided since key be arranged so that rotor stressed key root and the keyway root of mainly concentrating on, the impeller bearing capacity is reduced, very easily fatigue failure of impeller during work, load can not withstand shocks, key takes place pressed erosion, fracture, keyway distortion and roll the key phenomenon, produce eccentric between impeller and the rotating shaft, uneven, the generation of phenomenons such as vibration, also make rotor unloading process of the present utility model simple relatively simultaneously, the coaxality of impeller and rotating shaft is good, good airproof performance, vibrate little etc., also greatly reduce simultaneously owing to rotary blade is directly installed in the rotating shaft of drive motor and causes the long rotating shaft that makes that brings of cantilever segment of motor shaft to increase the negative influence of bringing for the rigidity of axle by the natural bow that deadweight produces.
When rotary blade 3 is multi-stage impeller 3 more than 2 grades or 2 grades, being installed in a drive motor rotating shaft one end with 2 grades of impeller 3 series aiding connections shown in Figure 1 is example, between this multi-stage impeller 3, be provided with positioning adapter 4, this positioning adapter 4 is fixed in the rotating shaft 2 of described motor by the interference orientation type on the one hand, as shown in the figure the interference locating face 341 between impeller and the positioning adapter; Form between the impeller 3 that its front and rear end is adjacent on the other hand and can transmit the second transmission of torque face 304 that holds out against moment, for make multi-stage impeller 3 can under the effect that holds out against moment that locking mechanism applies by positioning adapter 4 and and impeller 3 between the transmission of torque face can better be pressed on vertically on the radial flange 21 of rotating shaft 2, also be formed with the first transmission of torque face 52 between one-level impeller and the locking mechanism.For further improving transmission effect and impeller 3 more fastening the leaning on rotating shaft 2 flanges 21 that hold out against moment, as shown in Figure 1, formation can be transmitted the 3rd transmission of torque face 302 that holds out against moment between the rotating shaft 2 of the part of the wheel hub inner peripheral surface of impeller and its relevant position and the flange.
Above-mentioned each transmission of torque face relies on and holds out against the frictional force transmission that moment exerts oneself to produce between the square transfer function face and hold out against moment, preferably, friction factor when transmission holds out against moment is between 0.10～0.35, for improving the effect that holds out against from the impeller 3 of locking mechanism, far away more from locking nut 6, suitable bigger more of the friction factor of transmission of torque face.Simultaneously, the selection of friction factor also will be considered the character of material, and the preferred multi-stage impeller of the application adopts aluminum alloy, and rotor adopts forged steel, and this moment, friction factor can be preferably 0.25.
Hold out against the transmission effect of moment and the degree of combining closely between the transmission of torque face for further improving, further preferred, first and/or the second transmission of torque face and/or the 3rd transmission of torque mask have certain gradient, and be preferred, and this gradient is spent between 25 degree 7.Alternative or further preferred, first and/or the second transmission of torque face and/or the 3rd transmission of torque mask have the convex-concave cooperating structure that increases the friction force effect, so not only can make the efficient of transmission of torque higher, also can make to have each other between the moment transfer surface better to compress effect.
For make positioning adapter 4 with its before and after between impeller 3 cooperate tightr, coaxality is higher, as shown in Figure 1, the utility model forms first axial ledge 41 at the front-end face of positioning adapter 4, and the inner peripheral surface of the wheel hub of the impeller 3 that is adjacent is realized compression fit radially; Easy for installation for assembling, the compression fit between the wheel hub of the impeller 3 that this first axial ledge 41 is adjacent is an interference fit; Further preferred, the ear end face of described positioning adapter 4 forms second axial ledge 42, and the inner peripheral surface of the wheel hub of the impeller 3 that this second axial ledge is adjacent is a Spielpassung, as shown in Figure 1, and Spielpassung face 342 between the two; Further preferred, the outer peripheral surface of described positioning adapter is formed with and is beneficial to the arc transition section that the refrigerant fluid enters the rear end impeller, tangent connection between the wheel hub of the impeller that this arc transition section is adjacent.The utility model is taken all factors into consideration the function that makes lining not only have axially locating to lining this, and also have the guiding fluid and enter effect in the impeller that is adjacent with as far as possible little loss, be to achieve many things at one stroke, brought unforeseeable technique effect.
Front side at multi-stage impeller 3 also is the front end of one-level impeller 3, locking mechanism is set, preferred locking mechanism is the locking nut 6 that is positioned at one-level impeller hub front end that is arranged on the rotor 2345, applies with positioning adapter 4 to described multi-stage impeller 3 by this locking nut 6 and holds out against moment.
Because the setting of locking nut 6 can influence flowing of impeller 3 inlet stream, locking nut 6 outer surfaces have and the suitable streamline shape of air-flow airintake direction; Preferably, the outer peripheral surface of locking nut is formed with and is beneficial to the arc transition section that fluid enters the one-level impeller, tangent connection between the wheel hub of the one-level impeller that this arc transition section is adjacent; Preferably, the outer surface of described locking nut 6 air flow inlet sides is an arc surface; Preferably, as shown in Figure 3, the front end of the outer surface of described locking nut 6 air flow inlet sides forms water conservancy diversion rib with certain guide functions or guiding gutter so that charge air flow is more perfect, reduces flow losses.
Consider that simultaneously impeller 3 directly is installed to the direct connection structure of machine shaft 2, because direct connection construction rotor 2345 is long, for shortening the length of machine shaft 2 cantilever segments as far as possible, here the thread section before the locking nut 6 is shortened, but because thread section shortens, can not as conventional centrifuge, utilize screw thread to pass through the mode that the hydraulic pressure frock is elongated locking nut 6 to rotor 2345 again, need the extra frock of making that nut is applied required locking torque.
As the mobility status of Fig. 2 a direct connection centrifuge locking back charge air flow and the conventional centrifuge locking shown in Fig. 2 b afterwards the charge air flow mobility status contrast as seen, the application can improve the influence of 6 pairs of inlet stream of locking nut greatly to the improvement of locking nut 6, even can also realize certain guide functions when water conservancy diversion rib or guiding gutter are set on it.
The utility model is taken all factors into consideration locking nut this to be made locking nut not only have conventional locking function also to have the guiding fluid and enter effect in the impeller with as far as possible little loss, be to achieve many things at one stroke, brought unforeseeable technique effect.
Because compressor has saved gear speedup case, key and keyway, has the following advantages:
(1) because the rated efficiency height of DC frequency-changing synchronous machine itself, and do not have the geared machine loss again, so improved the full load performance of centrifuge compressor;
(2) owing to there is not the gear mechanism transmission, the compressor operating noise is very low, generally at 70～80 decibels, than low about 10 decibels of conventional centrifuge, saves the sound arrester that is provided with for noise reduction in engineering is used, and saves construction investment;
(3) owing to there is not the overdrive gear structure, compressor contour structure size and weight reduce greatly, and overall structure is compact more, thereby also reduces the compressor cost;
(4) owing to do not have key and keyway arrangements, concentricity and running accuracy between compressor impeller and the rotating shaft increase greatly, and the transmission of torque rubbing surface is stressed to be evenly distributed, and whole manufacturing procedure reduces, thereby also reduces cost for manufacturing compressor;
Need to prove at last:
Although describe and illustrate various creative aspect of the present utility model, notion and feature in this article, implement them in the exemplary embodiment by combination, but can in many alternate embodiments, use aspect different embodiments various, notion and feature, individually or in the mode of various combinations and sub-portfolio thereof.Unless be explicitly excluded in this article outside, combination that all are such and sub-portfolio intention all are in scope of the present utility model.
In addition, although may describe various preferred implementations in this article about various aspects of the present utility model, notion and feature, 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 exemplary configurations is not limited to comprise desired in all cases all features, unless clearly be set fourth as this situation.
Claims (37)
1. the high-velocity fluid dynamic power machine of a rotating speed more than 6000rpm, it comprises drive motor and rotor, rotor comprises the rotary blade of drive motor rotating shaft and convection cell acting, it is characterized in that: described rotary blade is directly installed in the rotating shaft of drive motor, and described rotary blade adopts no key Placement, be positioned at drive motor rotating shaft interference by hot pressing mode diametrically, the structure that is locked on axially compresses and leans on a radial flange of rotating shaft.
2. high-velocity fluid dynamic power machine as claimed in claim 1, it is characterized in that: described rotary blade is a multi-stage impeller, between this multi-stage impeller, be provided with positioning adapter, this positioning adapter is fixed on the interference orientation type in the rotating shaft of described motor by hot pressing mode on the one hand, forms between the impeller hub that its front and rear end is adjacent on the other hand and can transmit the second transmission of torque face that holds out against moment.
3. high-velocity fluid dynamic power machine as claimed in claim 2, it is characterized in that: described multi-stage impeller between the one-level impeller of front end and described locking mechanism, be formed with the first transmission of torque face, described multi-stage impeller between the impeller of rear end and described rotating shaft and radial flange thereof, be formed with the 3rd transmission of torque face.
4. high-velocity fluid dynamic power machine as claimed in claim 3 is characterized in that: the described first and/or second transmission of torque face and/or the 3rd transmission of torque mask have certain gradient; And/or described first and/or second transmission of torque face and/or the 3rd transmission of torque mask the convex-concave cooperating structure that increases the friction force effect is arranged.
5. high-velocity fluid dynamic power machine as claimed in claim 4 is characterized in that: the gradient of the described first and/or second transmission of torque face and/or the 3rd transmission of torque face is spent between 25 degree 7.
6. as each described high-velocity fluid dynamic power machine of claim 2-5, it is characterized in that: the front-end face of described positioning adapter forms first axial ledge, and the inner peripheral surface of the wheel hub of the impeller that is adjacent is realized compression fit radially.
7. high-velocity fluid dynamic power machine as claimed in claim 6 is characterized in that, the compression fit between the wheel hub of the impeller that described first axial ledge is adjacent is an interference fit.
8. high-velocity fluid dynamic power machine as claimed in claim 6 is characterized in that the ear end face of described positioning adapter forms second axial ledge, and the inner peripheral surface of the wheel hub of the impeller that this second axial ledge is adjacent is a Spielpassung.
9. high-velocity fluid dynamic power machine as claimed in claim 6, the outer peripheral surface that it is characterized in that described positioning adapter is formed with to be beneficial to and improves fluid and enter the arc transition section that flows of impeller thereafter, tangent connection between the impeller hub that this arc transition section is adjacent.
10. as each described high-velocity fluid dynamic power machine of claim 3-5, it is characterized in that: described locking mechanism is to be arranged on the epitrochanterian distolateral locking nut of one-level impeller eye that is positioned at, and applies with the location axle sleeve to described multi-stage impeller by this locking nut and holds out against moment.
11. high-velocity fluid dynamic power machine as claimed in claim 10, it is characterized in that, the outer peripheral surface of described locking nut is formed with and is beneficial to the arc transition section that fluid enters the acting of one-level impeller, tangent connection between the wheel hub of the one-level impeller that this arc transition section is adjacent.
12. high-velocity fluid dynamic power machine as claimed in claim 10 is characterized in that, the outer surface of described locking nut air flow inlet side has and the suitable streamline shape of air-flow airintake direction.
13. high-velocity fluid dynamic power machine as claimed in claim 12 is characterized in that, the outer surface of described locking nut air flow inlet side is an arc surface.
14. high-velocity fluid dynamic power machine as claimed in claim 13 is characterized in that, the front end of the outer surface of described locking nut air flow inlet side forms water conservancy diversion rib or the guiding gutter with certain guide functions.
15. high-velocity fluid dynamic power machine as claimed in claim 10, it is characterized in that: the locating washer that also is provided with increase power area of contact between described locking nut and the one-level impeller, described locating washer is formed with axial slotting face and the transmission of torque face radially stretched, the described axial slotting inner peripheral surface of stretching the wheel hub of face and one-level impeller is combined together, described transmission of torque face one side radially acts on the ear end face of one-level impeller, opposite side acts on described locking nut and accepts and transmit the moment that holds out against that described locking nut applies, and forms the described first transmission of torque face between described locating washer and the one-level impeller.
16. as each described high-velocity fluid dynamic power machine of claim 2-5, it is characterized in that: described each transmission of torque face utilizes the frictional force transmission between the acting surface, and friction factor is between 0.10～0.35.
17. high-velocity fluid dynamic power machine as claimed in claim 16 is characterized in that, and is far away more from locking nut, described each transmission of torque face friction factor is big more.
18. high-velocity fluid dynamic power machine as claimed in claim 16 is characterized in that, described multi-stage impeller adopts aluminum alloy, and forged steel is adopted in described rotating shaft, and friction factor is 0.25.
19. high-velocity fluid dynamic power machine as claimed in claim 6 is characterized in that: described each transmission of torque face utilizes the frictional force transmission between the acting surface, and friction factor is between 0.10～0.35.
20. high-velocity fluid dynamic power machine as claimed in claim 10 is characterized in that: described each transmission of torque face utilizes the frictional force transmission between the acting surface, and friction factor is between 0.10～0.35.
21. as each described high-velocity fluid dynamic power machine of claim 2-5, it is characterized in that: between described impeller and the rotating shaft, between impeller and the positioning adapter, the interference location amount of interference fit is 0.01～0.02mm between positioning adapter and the rotating shaft, the required gap of assembling, heating back is chosen by the H7/g6 of fit diameter, wherein the upper deviation of diameter is closed in the H7 assignment, the lower deviation of diameter is closed in the g6 assignment, and the interference fit diameter A between described impeller and positioning adapter, impeller and rotating shaft is all roughly between 30～60mm.
22. high-velocity fluid dynamic power machine as claimed in claim 6, it is characterized in that: between described impeller and the rotating shaft, between impeller and the positioning adapter, the interference location amount of interference fit is 0.01～0.02mm between positioning adapter and the rotating shaft, the required gap of assembling, heating back is chosen by the H7/g6 of fit diameter, wherein the upper deviation of diameter is closed in the H7 assignment, the lower deviation of diameter is closed in the g6 assignment, and the interference fit diameter A between described impeller and positioning adapter, impeller and rotating shaft is all roughly between 30～60mm.
23. as each described high-velocity fluid dynamic power machine of claim 7-9, it is characterized in that: between described impeller and the rotating shaft, between impeller and the positioning adapter, the interference location amount of interference fit is 0.01～0.02mm between positioning adapter and the rotating shaft, the required gap of assembling, heating back is chosen by the H7/g6 of fit diameter, wherein the upper deviation of diameter is closed in the H7 assignment, the lower deviation of diameter is closed in the g6 assignment, and the interference fit diameter A between described impeller and positioning adapter, impeller and rotating shaft is all roughly between 30～60mm.
24. high-velocity fluid dynamic power machine as claimed in claim 10, it is characterized in that: between described impeller and the rotating shaft, between impeller and the positioning adapter, the interference location amount of interference fit is 0.01～0.02mm between positioning adapter and the rotating shaft, the required gap of assembling, heating back is chosen by the H7/g6 of fit diameter, wherein the upper deviation of diameter is closed in the H7 assignment, the lower deviation of diameter is closed in the g6 assignment, and the interference fit diameter A between described impeller and positioning adapter, impeller and rotating shaft is all roughly between 30～60mm.
25. high-velocity fluid dynamic power machine as claimed in claim 16, it is characterized in that: between described impeller and the rotating shaft, between impeller and the positioning adapter, the interference location amount of interference fit is 0.01～0.02mm between positioning adapter and the rotating shaft, the required gap of assembling, heating back is chosen by the H7/g6 of fit diameter, wherein the upper deviation of diameter is closed in the H7 assignment, the lower deviation of diameter is closed in the g6 assignment, and the interference fit diameter A between described impeller and positioning adapter, impeller and rotating shaft is all roughly between 30～60mm.
26. high-velocity fluid dynamic power machine as claimed in claim 21, it is characterized in that: between described impeller and the rotating shaft, between impeller and the positioning adapter, the interference location amount of interference fit is 0.01～0.02mm between positioning adapter and the rotating shaft, the required gap of assembling, heating back is chosen by the H7/g6 of fit diameter, wherein the upper deviation of diameter is closed in the H7 assignment, the lower deviation of diameter is closed in the g6 assignment, and the interference fit diameter A between described impeller and positioning adapter, impeller and rotating shaft is all roughly between 30～60mm.
27. as each described high-velocity fluid dynamic power machine of claim 1-5, it is characterized in that: described impeller is a both stage impellers or greater than 2 grades multi-stage impeller, this multi-stage impeller series aiding connection is installed in an end of drive motor rotating shaft.
28. high-velocity fluid dynamic power machine as claimed in claim 6 is characterized in that: described impeller is a both stage impellers or greater than 2 grades multi-stage impeller, this multi-stage impeller series aiding connection is installed in an end of drive motor rotating shaft.
29. high-velocity fluid dynamic power machine as claimed in claim 10 is characterized in that: described impeller is a both stage impellers or greater than 2 grades multi-stage impeller, this multi-stage impeller series aiding connection is installed in an end of drive motor rotating shaft.
30. high-velocity fluid dynamic power machine as claimed in claim 16 is characterized in that: described impeller is a both stage impellers or greater than 2 grades multi-stage impeller, this multi-stage impeller series aiding connection is installed in an end of drive motor rotating shaft.
31. high-velocity fluid dynamic power machine as claimed in claim 21 is characterized in that: described impeller is a both stage impellers or greater than 2 grades multi-stage impeller, this multi-stage impeller series aiding connection is installed in an end of drive motor rotating shaft.
32. as each described high-velocity fluid dynamic power machine of claim 1-5, it is characterized in that: described high-velocity fluid dynamic power machine is the high-speed centrifugal compressor.
33. high-velocity fluid dynamic power machine as claimed in claim 6 is characterized in that: described high-velocity fluid dynamic power machine is the high-speed centrifugal compressor.
34. high-velocity fluid dynamic power machine as claimed in claim 10 is characterized in that: described high-velocity fluid dynamic power machine is the high-speed centrifugal compressor.
35. as each described high-velocity fluid dynamic power machine of claim 1-5, it is characterized in that: the rotating speed of described high-velocity fluid dynamic power machine is between 7000rpm～20000rpm.
36. high-velocity fluid dynamic power machine as claimed in claim 6 is characterized in that: the rotating speed of described high-velocity fluid dynamic power machine is between 7000rpm～20000rpm.
37. high-velocity fluid dynamic power machine as claimed in claim 10 is characterized in that: the rotating speed of described high-velocity fluid dynamic power machine is between 7000rpm～20000rpm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220151354 CN203081853U (en) | 2012-04-02 | 2012-04-02 | High-speed fluid power machine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220151354 CN203081853U (en) | 2012-04-02 | 2012-04-02 | High-speed fluid power machine |
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| CN203081853U true CN203081853U (en) | 2013-07-24 |
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| CN 201220151354 Expired - Fee Related CN203081853U (en) | 2012-04-02 | 2012-04-02 | High-speed fluid power machine |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103362860A (en) * | 2012-04-02 | 2013-10-23 | 珠海格力电器股份有限公司 | High-speed hydrodynamic machine and composition method and assembly method of rotor of high-speed hydrodynamic machine |
| CN105683502A (en) * | 2013-12-11 | 2016-06-15 | 三菱重工业株式会社 | Rotating body and method for manufacturing rotating body |
| CN110360149A (en) * | 2018-04-10 | 2019-10-22 | 南通大通宝富风机有限公司 | Impeller and the both vapor compression equipment for using the impeller |
-
2012
- 2012-04-02 CN CN 201220151354 patent/CN203081853U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103362860A (en) * | 2012-04-02 | 2013-10-23 | 珠海格力电器股份有限公司 | High-speed hydrodynamic machine and composition method and assembly method of rotor of high-speed hydrodynamic machine |
| CN105683502A (en) * | 2013-12-11 | 2016-06-15 | 三菱重工业株式会社 | Rotating body and method for manufacturing rotating body |
| US10578116B2 (en) | 2013-12-11 | 2020-03-03 | Mitsubishi Heavy Industries, Ltd. | Rotational body and method for manufacturing the same |
| CN110360149A (en) * | 2018-04-10 | 2019-10-22 | 南通大通宝富风机有限公司 | Impeller and the both vapor compression equipment for using the impeller |
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