CN218062704U - Suspension centrifugal compressor and air conditioning system - Google Patents
Suspension centrifugal compressor and air conditioning system Download PDFInfo
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- CN218062704U CN218062704U CN202222386231.3U CN202222386231U CN218062704U CN 218062704 U CN218062704 U CN 218062704U CN 202222386231 U CN202222386231 U CN 202222386231U CN 218062704 U CN218062704 U CN 218062704U
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Abstract
The utility model discloses a suspension centrifugal compressor, including main shaft, fixed mounting main epaxial impeller device and cover are located the radial gas bearing and the axial gas bearing of main shaft, the main shaft extends the setting from top to bottom, impeller device acts on when rotating main epaxial axial thrust upwards. Because the main shaft extends up and down, the axial upward thrust can play a role in overcoming the gravity of the main shaft, so that the gravity of the main shaft is less born by the axial bearing, and the working pressure of the axial bearing is effectively reduced. The utility model also discloses an air conditioning system of including above-mentioned suspension centrifugal compressor.
Description
Technical Field
The utility model relates to a compressor technical field, more specifically say, relate to a suspension centrifugal compressor and an air conditioning system including above-mentioned suspension centrifugal compressor.
Background
The existing air suspension centrifugal compressor is generally horizontally arranged, an air bearing is sleeved on a main shaft, the radial stress of the main shaft needs to overcome the self weight of the air bearing in the operation process, and the stress source can be the introduction of external air supply or internal compressor exhaust for an aerostatic bearing and is an air wedge for air compression for an aerostatic bearing; axial force can be offset due to the introduction of the support of the gas bearing, but radial force cannot be offset due to the self gravity of the main shaft; when the gas supply amount is insufficient, the problem of insufficient reliability is caused, and when the gas supply amount is satisfied, the loss is increased, and the efficiency of the whole machine is reduced.
In summary, how to effectively solve the problem of excessive bearing pressure on the spindle is a problem that needs to be solved urgently by those skilled in the art.
SUMMERY OF THE UTILITY MODEL
In view of this, the utility model provides a suspension centrifugal compressor, this suspension centrifugal compressor can solve the too big problem of bearing capacity on the main shaft effectively, the utility model provides an air conditioning system including above-mentioned suspension centrifugal compressor.
The utility model provides a following technical scheme:
the utility model provides a suspension centrifugal compressor, includes main shaft, fixed mounting be in epaxial impeller device of main shaft and cover are located the radial gas bearing and the axial gas bearing of main shaft, the main shaft extends the setting from top to bottom, the impeller device is used in when rotating axial thrust on the main shaft is upwards.
When the suspension centrifugal compressor is used, when the impeller device starts to rotate to compress air or other gases, the impeller of the impeller device can form axial upward thrust due to the air pressure effect, and the axial upward thrust can play a role in overcoming the gravity effect of the main shaft because the main shaft extends up and down, so that the axial bearing with less gravity of the main shaft bears, and the working pressure of the axial bearing is effectively reduced. In conclusion, the suspension centrifugal compressor can effectively solve the problem of overlarge bearing pressure on the main shaft.
Preferably, the impeller device is provided with a plurality of impellers, and each impeller of the impeller device rotates to act on the main shaft with the total axial thrust upwards.
Preferably, each impeller of the impeller device acts on the main shaft in an upward direction when rotating.
Preferably, each impeller of the impeller device is axially air-in and radially air-out.
Preferably, the impellers at the two ends of the main shaft are oppositely arranged or oppositely arranged.
Preferably, each impeller of the impeller device is axially downward air inlet.
Preferably, each impeller of the impeller device is arranged at one end of the main shaft or at two ends of the main shaft respectively.
Preferably, the main shaft is arranged vertically.
In order to achieve the second objective, the present invention further provides an air conditioning system, which comprises any one of the above-mentioned suspension centrifugal compressors, including an evaporator and a condenser, wherein the suspension centrifugal compressor is communicated with the evaporator and the condenser. Since the above-mentioned suspension centrifugal compressor has the above-mentioned technical effects, an air conditioning system having the suspension centrifugal compressor should also have corresponding technical effects.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the description below are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a suspension centrifugal compressor according to an embodiment of the present invention;
fig. 2 is a schematic structural view of an impeller provided in an embodiment of the present invention, which is away from each other;
fig. 3 is a schematic structural view of the impeller provided by the embodiment of the present invention;
fig. 4 is a schematic structural view of the impeller provided in the embodiment of the present invention in the same direction;
fig. 5 is a schematic structural diagram of the impeller provided by the embodiment of the present invention at the same side.
The drawings are numbered as follows:
the device comprises a main shaft 1, an impeller device 2, a volute 3, a stator 4, a radial gas bearing 5, an axial gas bearing 6 and an impeller 21.
Detailed Description
The embodiment of the utility model discloses suspension centrifugal compressor to solve the too big problem of bearing capacity on the main shaft effectively.
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts all belong to the protection scope of the present invention.
Referring to fig. 1-5, fig. 1 is a schematic structural view of a suspension centrifugal compressor according to an embodiment of the present invention; fig. 2 is a schematic structural view of an impeller provided in an embodiment of the present invention, which is away from each other; fig. 3 is a schematic structural view of the impeller provided by the embodiment of the present invention; fig. 4 is a schematic structural view of the impeller provided by the embodiment of the present invention in the same direction; fig. 5 is a schematic structural diagram of the impeller disposed on the same side provided by the embodiment of the present invention.
In some embodiments, as shown in fig. 1, there is provided a suspension centrifugal compressor comprising at least one, more, or even all of the following structures: the main shaft 1, the impeller device 2, the radial gas bearing 5 and the axial gas bearing 6, but may of course also comprise some other structure, such as the stator 4, the volute 3, etc. For example, the compressor can comprise an electric motor part, a pneumatic part and a mechanical part. Wherein the motor part may for example comprise a stator 4, a coil, a rotor. The pneumatic part can comprise an impeller 21, a volute 3, a main shaft 1 and a bearing, wherein the main shaft 1 is a moving part for connecting the impeller 21 and a motor rotor; the bearing comprises a radial supporting part and an axial supporting part, namely the radial gas bearing 5 and the axial gas bearing 6 which are used for supporting the main shaft 1 and the impeller 21 and the rotor which are connected with the main shaft; the volute 3 is a pressure chamber structure having an inlet and an outlet, and is capable of collecting gas generated in the impeller 21 to flow to the exhaust port. Wherein the mechanical part is a related connecting and sealing structure. It should be noted that, the compressor may be a combination of the above partial structures, or may even be a combination of all the structures, and specifically, the compressor may be set as required.
Wherein the impeller device 2 is fixedly installed on the main shaft 1, wherein the impeller device 2 may include one or more impellers 21 so as to drive the impellers 21 thereon to rotate when the main shaft 1 rotates. And wherein the rotation of the main shaft 1 may be driven by the coils in the stator 4, but also by other structures. Wherein impeller 21 can be with main shaft 1 integrated into one piece, also can dismantle fixed connection, if impeller 21 cover establish on main shaft 1, and between the key-type connection to pass through nut locking in the axial, impeller axial one side can be supported with the shoulder of main shaft 1 promptly, and the other end supports with the nut of threaded connection on the main shaft, and after dismantling the nut, wherein impeller 21 can be followed main shaft 1 and detached. Of course, reference may also be made to the prior art for the connection between the impeller 21 and the main shaft 1.
Wherein the main shaft 1 is sleeved with a radial gas bearing 5 and an axial gas bearing 6 for radial support by the radial gas bearing 5 and axial support by the axial gas bearing 6. Wherein the radial gas bearing 5 and the axial gas bearing 6 can be respectively selected from a dynamic pressure gas bearing and a static pressure gas bearing according to requirements. Of course in some other embodiments, the main shaft 1 may be provided with ball bearings to act as radial and axial bearings, respectively.
The main shaft 1 extends up and down, is generally vertically arranged, and can be inclined, for example, inclined upward, specifically, can be arranged as required. And the axial thrust acting on the main shaft 1 when the impeller device 2 rotates is upward, so that the effect of overcoming the gravity of the main shaft 1 can be achieved. It should be noted that, when the main shaft 1 is vertically arranged, the axial thrust acting on the main shaft 1 when the impeller device 2 rotates is upward, which is vertical upward; if the spindle 1 is arranged obliquely, the axial thrust is inclined upwards, and if the axial thrust is inclined upwards, because of the vertically upwards component in the vertical direction, a part of the gravity of the spindle 1 can also be overcome. For better overcoming the weight of the spindle 1, the spindle 1 is preferably arranged vertically here.
It should be noted that, when the impeller device 2 rotates, the impeller 21 receives an axial thrust, and the radial thrust is transmitted to the main shaft 1, so that the direction of the thrust of the impeller 21 acting on the main shaft 1, that is, the thrust on the main shaft 1 is controlled upward in the axial direction, can be effectively controlled by adjusting the arrangement state of the impeller 21. It should be noted that if the force applied to the bottom surface by the whole machine is not changed, the wind pressure applied to the impeller 21 can push the casing or the base part of the whole machine in the opposite direction to maintain the force balance.
It should be further noted that the axial thrust generated by the impeller 21 mainly has the following two reasons, but is not limited to the following two reasons:
one reason for this is: because of the internal gas leakage, a pressure difference is generated between the two sides of the wheel cover and the wheel back of the impeller 21; and pressure F = ps; p represents gas pressure, and S represents an action area or an axial projection area along the axial direction; the pressure on the wheel cover side is internal leakage generated between exhaust and suction, namely, the pressure difference between the air outlet and the inlet of the impeller 21; i.e. as shown in fig. 2, af = Fa wheel back-Fa wheel cover; fa wheel cover = Pa Sa, where "=" denotes product, where "=" denotes equal sign; pa is the pressure between the outlet of the impeller 21 and the inlet of the impeller 21; sa is the axial component of the wheel cover; fa wheel back = Pc × Sc; pc is the pressure between the outlet of the impeller 21 and the inner cavity of the motor; sc is the sectional area of the wheel back perpendicular to the main shaft 1; the sizes of the Fa wheel back and the Fa wheel cover are influenced by pressure intensity and sectional area together, and the sizes are related to leakage amount, operation rotating speed or pressure ratio, designed section size and the like caused by fit clearance and are determined according to specific conditions. Therefore, the corresponding Fa wheel back or Fa wheel cover can be adjusted according to the up-down position relation of the wheel cover and the wheel back, so that the comprehensive acting force is axially upward.
Another reason is that: according to the aerodynamic concept, the inlet direction and/or outlet direction of the impeller 21 is axial, for example. If the air intake direction is axial, it may be axial upward, or axial downward, and the axial direction is air intake upward, the impeller 21 may form downward axial thrust, and the axial direction is air intake downward, and the impeller 21 may form upward axial thrust. If the air outlet direction is axial, the air outlet direction may be axial upward or axial downward, if the air outlet is axial upward, the impeller 21 may form downward axial thrust, and if the air outlet is axial downward, the impeller 21 may form downward axial thrust. In order to better achieve the above effect, if the impeller 21 can be axially and downwardly charged and axially and downwardly discharged, the design principle of the propeller of the helicopter can be referred to achieve the above effect, and thus the above problem can be better overcome. Of course, as shown in fig. 1 to 5, each impeller 21 of the impeller device 2 may be axially air-inlet and radially air-outlet.
Both of the above two reasons are that the axial thrust direction of the impeller device 2 can be changed to be the upward direction through corresponding adjustment of the internal structure, and it should be noted that one or more parameters or structures can be selected for improvement, so that after the integration, the axial thrust of the impeller 21 of the impeller device 2 to the main shaft 1 is upward. In practical design, the axial direction of the axial force of the impeller 21 can be changed according to the current axial direction of the axial force, and if the axial direction is downward, the axial direction of the axial force can be changed based on the above reasons, such as changing the direction of the air inlet and outlet, changing the size of the wheel cover and the wheel back, and changing the axial direction of the axial force, or even further changing the size of the axial force.
In some embodiments, when the above-mentioned suspension centrifugal compressor is used, when the impeller device 2 starts to rotate to compress air, at this time, the impeller 21 of the impeller device 2 will form an axially upward thrust due to the action of air pressure, and because the main shaft 1 extends up and down, the axially upward thrust can play a role in overcoming the gravity of the main shaft 1, so that the axial bearing with less gravity of the main shaft 1 bears, and the working pressure of the axial bearing is effectively reduced, for example, the axial gas bearing 6 can effectively reduce the working pressure of the axial gas bearing 6 in an operating state, and further can reduce the air supply amount, so as to play a role in reducing energy consumption, and improve the overall efficiency, and meanwhile, the radial bearing does not need to bear the gravity again, so that the working pressure can also be reduced, and the minimization of vibration is brought about. In conclusion, the suspension centrifugal compressor can effectively solve the problem of overlarge bearing pressure on the main shaft 1.
In some embodiments, as shown in fig. 1 to 5, it is possible to make the impeller device 2 have a plurality of impellers 21, and it is only necessary that the total axial thrust acting on the main shaft 1 when the impellers 21 of the impeller device 2 rotate is upward, and it is preferable that the total axial thrust acting on the main shaft 1 when the impellers 21 of the impeller device 2 rotate is close to the gravity of the main shaft 1. That is, the vertical direction component of the force acting on the main shaft 1 as each impeller 21 is: f1, F2, 8230, (8230), fn, and at least part of the direction is upward. Then F1+ \8230 \ 8230 ++ Fn + G =0, where G is the gravity and the direction is downward, n is the number of impellers 21 on the same main shaft 1, and n ≧ 1. That is, the axial thrust acting on the main shaft 1 when one portion of the impeller 21 of the impeller device 2 is rotated is directed downward, and the axial thrust acting on the main shaft 1 when the other portion of the impeller 21 of the impeller device 2 is rotated is directed upward.
It should be noted that:
for a one-stage compression system: that is, there may be only one impeller 21, when the back pressure of the impeller 21 is greater than the pressure of the wheel cover, the force receiving direction is from the wheel back to the wheel cover, and the pressure difference is Δ F1; or when the back pressure of the impeller 21 is smaller than the pressure of the wheel cover, the stress direction is from the wheel cover to the wheel back; the pressure difference is-DeltaF 1; the stress direction of the pressure difference (delta F1 or-delta F1) is required to be opposite to the gravity G direction all the time; to counteract a portion of the effects of gravity.
For a multi-stage compression system, i.e., having more than two impellers 21, the impellers 21 may be arranged in an opposed manner (i.e., the two impellers 21 are mounted in opposite directions) or in the same direction; or a partially co-directional and partially counter-mixed manner; the direction of the axial pressure borne by at least one impeller 21 is opposite to the direction of the gravity borne by the impeller, so that the direction of the resultant force borne by the impeller is opposite to the direction of the gravity; it is also possible that one or more of the impellers 21 are subjected to a force in the opposite direction to the force of gravity and the remaining impellers 21 are subjected to the same force of gravity, in order to minimize the component in the axial direction of the resultant force of the pressure of the impellers 21 and the force of gravity of the main shaft 1. When there are multiple stages of impellers 21, it is possible to have at least one set of two stages of impellers 21: the higher stage impeller 21 is smaller in geometry than the lower stage impeller 21. Preferentially designing the thrust and gravity of the impeller 21 in the range of 50 +/-20% of the load working condition, and considering the effect of minimizing or mutually offsetting the thrust and the gravity; in order to minimize the axial supporting force under the common working condition, the common working condition loss is reduced.
Wherein the impeller 21 of the lower one-level of impeller 21 of higher one-level is littleer in the geometric dimensions, specifically, can be according to: q m ＝Q v * Rho; wherein Q m Mass flow (compression process is not changed), Q v Is the volume flow, ρ is the gas density; q v V × S; v is the gas linear velocity and S is the flow cross-sectional area (or exit cross-section); v = W R; w =2 π f; w is the gas angular velocity, R is the impeller radius; f is the rotation frequency.
The above expressions can also be arranged into one expression; namely Q m ＝2πf*R*S*ρ；
Mass flow Q in the system m Impeller compression one stage below under substantially constant conditionsThen, the volume of the compressed gas is reduced, and the density is increased; corresponding to the same coaxial rotating speed, f is unchanged, namely W is unchanged, V is reduced or S is reduced, and V is reduced, namely corresponding to the radius reduction of the impeller; the R and the outlet section S of the impeller which is usually higher by one stage are simultaneously reduced and adjusted; otherwise, when the compression is performed in the first-stage compression with the same size and the same height, the problems that the other losses such as eddy current loss and the like are easily caused under the large diameter and the large section of the internal fluid, the efficiency is reduced and the cost is increased are easily caused.
In some embodiments, the axial thrust acting on the main shaft 1 when each impeller 21 of the impeller device 2 rotates is upward, which effectively enlarges the total thrust to better ensure that the total thrust is close to the gravity of the main shaft 1.
In some embodiments, as shown in fig. 1-3, each impeller 21 of the impeller device 2 is axially air-in and radially air-out. At this time, the impellers 21 at the two ends of the main shaft 1 may be oppositely arranged or arranged oppositely, that is, the axial air intake directions of the impellers 21 at the two ends of the main shaft 1 are opposite. Wherein
The relative arrangement is that, as shown in fig. 3, the air inlet direction of the impeller 21 at the lower end is axially downward, and the air inlet direction of the impeller 21 at the upper end is axially upward; the opposite arrangement is that, as shown in fig. 1-2, the air inlet direction of the impeller 21 at the lower end is axially upward, and the air inlet direction of the impeller 21 at the lower end is axially downward.
In some embodiments, as shown in fig. 4-5, each impeller 21 of the impeller device 2 may be axially downward-directed. Wherein each impeller 21 of the impeller device 2 is arranged at one end of the main shaft 1 or at both ends of the main shaft 1, respectively. As shown in fig. 4, wherein each impeller 21 of the impeller device 2 is respectively arranged at both ends of the main shaft 1, as shown in fig. 5, wherein each impeller 21 of the impeller device 2 is arranged at one end of the main shaft 1.
In some embodiments, it is preferred wherein the main shaft 1 is arranged vertically. The radial force is set in the horizontal direction; the source of the radial force may be an externally supplied gas or an internally self-forming gas wedge.
Based on the suspension centrifugal compressor that provides in the above-mentioned embodiment, the utility model also provides an air conditioning system, this air conditioning system include arbitrary suspension centrifugal compressor in the above-mentioned embodiment, still include evaporimeter and condenser suspension centrifugal compressor intercommunication is in the evaporimeter with between the condenser. Since the air conditioning system employs the suspension centrifugal compressor in the above embodiment, please refer to the above embodiment for the beneficial effect of the air conditioning system.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (9)
1. The utility model provides a suspension centrifugal compressor, includes main shaft, fixed mounting be in epaxial impeller device of main shaft and cover are located the radial gas bearing and the axial gas bearing of main shaft, its characterized in that, the main shaft extends the setting from top to bottom, when impeller device rotates, is used in epaxial axial thrust upwards.
2. The levitation centrifugal compressor of claim 1, wherein the impeller device has a plurality of impellers, and each impeller of the impeller device rotates with an axial total thrust force acting on the main shaft upward.
3. The levitation centrifugal compressor of claim 2, wherein each impeller of the impeller device rotates with an axial thrust acting on the main shaft in an upward direction.
4. The levitation centrifugal compressor as recited in claim 3, wherein each impeller of the impeller device is axial inlet and radial outlet.
5. The levitation centrifugal compressor of claim 4, wherein the impellers at both ends of the main shaft are disposed opposite or apart.
6. The suspension centrifugal compressor of claim 4, wherein each impeller of the impeller means is axially downwardly fed air.
7. The levitation centrifugal compressor as recited in claim 6, wherein each impeller of the impeller device is disposed at one end of the main shaft or at both ends of the main shaft, respectively.
8. The levitation centrifugal compressor as recited in any one of claims 1-7, wherein the main shaft is vertically disposed.
9. An air conditioning system comprising an evaporator and a condenser, further comprising a suspending centrifugal compressor according to any one of claims 1 to 8, said suspending centrifugal compressor communicating between said evaporator and said condenser.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202222386231.3U CN218062704U (en) | 2022-09-07 | 2022-09-07 | Suspension centrifugal compressor and air conditioning system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202222386231.3U CN218062704U (en) | 2022-09-07 | 2022-09-07 | Suspension centrifugal compressor and air conditioning system |
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| CN218062704U true CN218062704U (en) | 2022-12-16 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024051099A1 (en) * | 2022-09-07 | 2024-03-14 | 深圳市英维克科技股份有限公司 | Suspension centrifugal compressor and air conditioner system |
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2022
- 2022-09-07 CN CN202222386231.3U patent/CN218062704U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024051099A1 (en) * | 2022-09-07 | 2024-03-14 | 深圳市英维克科技股份有限公司 | Suspension centrifugal compressor and air conditioner system |
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