CN204716545U - A kind of new type of compression device - Google Patents

Abstract

The utility model provides a kind of novel fluid compression set, this technology is primarily of housing, turbine, worm screw is formed, described turbine can be that single blade face is closed centrifugal turbine and is arranged in housing, described worm screw is tapered to be positioned on the wheel radius surface of housing turbine, spiral snail on described worm screw convex with the whirlpool groove on turbine mutually to embedding coupling, leaf on described turbine is convex recessed mutually to embedding coupling with the spiral snail on worm screw, keep certain interval each other, described turbine central shaft there is angular wheel follow the angular wheel on the centripetal end of worm screw to engage each other, angular wheel on the centripetal end of described worm screw is identical with the rotating ratio of turbine with worm screw with the rotating ratio of the angular wheel on turbine central shaft.Described turbine, worm screw are surrounded sealing by housing, the housing of described worm screw outer edge place turbine rotation prime direction side has outlet, the convex side body of described turbine inner circle circle centre position leaf has import.

Description

A kind of new type of compression device

Technical field

What the present invention relates to is a kind of compressed machinery, especially fluid compressing device.

Background technique

In the prior art, scroll compressor, helical-lobe compressor and centrifugal compressor is had closest to this technology.Scroll type air compressor forms by the dynamic and static vortex of function side and molded line is mutually meshing.In air-breathing, compression, exhaust work process, fixed scroll is fixed in frame, Moving plate is driven by eccentric shaft and is restricted by anti-automatic mechanism, around quiet dish basic circle center, make the Plane Rotation of very minor radius, gas is by the periphery of air-filtering wicking dish in meditation, and along with eccentric shaft rotates, then gas formed somely to be discharged by the axial bore at quiet dish position progressively compressing in crescent shape compression chamber continuously sound dish is meshing.Screw compressor cylinder is built with a pair intermeshing spirality negative and positive rotor, and two rotors have several spill tooth, both mutual counterrotatings.Gap between rotor and between casing and rotor is only 5 ~ 10, main rotor is also known as male rotor or convex rotor, by being motoring by motor or motoring majority, another rotor is that the oil film formed by oil spout by main rotor is driven also known as female rotor or recessed rotor, or is driven by the synchromesh gear of main rotor end and recessed rotor-end.So there is no Metal Contact in theory in driving.The length of rotor and diameter determine compressor air-discharging amount and flow and exhaust pressure, and rotor is longer, and pressure is higher; Root diameter is larger, and flow is larger.Centrifugal compressor is used for impeller that the critical piece of pressurized gas is High Rotation Speed and the Diffuser that flow area increases gradually.In brief, the working principle of centrifugal compressor is by impeller to gas work done, in the runner of impeller and Diffuser, utilizes centrifugal boosting and reduction of speed diffusion action, mechanical energy is converted to the pressure energy of gas.In sum, scroll compressor is not suitable for large discharge compression device uses, but the higher accuracy of manufacturing of efficiency of screw rod compressor requires also high, therefore manufacture cost is also high, centrifugal compressor is applicable to large discharge gas transmission requirement, but be not suitable for the little and pressure ratio of throughput require high occasion and low speed time efficiency lower, delivery pressure is lower.The deficiency that Here it is existing for prior art.

Summary of the invention

Technical problem to be solved by this invention is exactly for the deficiency existing for prior art, and provides a kind of big-flow high-pressure that can be applicable to contract than a kind of new type of compression device requiring can to export when the slow-speed of revolution works elevated pressures, high efficiency, low cost.

This programme is achieved by the following technical measures: primarily of housing, turbine, worm screw is formed, described turbine can be that single blade face is closed centrifugal turbine and is arranged in housing, also can be that the single closed centrifugal turbine in double leaf face is arranged in housing, described worm screw is tapered to be positioned on the wheel radius surface of housing turbine, spiral snail on described worm screw convex with the whirlpool groove on turbine mutually to embedding coupling, leaf on described turbine is convex recessed mutually to embedding coupling with the spiral snail on worm screw, it remains certain interval each other, its gap is generally between five to ten, also can remain between one to two ten, can also put the wider efficiency in wider only gap is lower, specifically determine according to machining accuracy, leaf on described turbine convex spiral snail with the spiral snail on worm screw on recessed and worm screw is convex to be not in contact with each other in clearance seal with between the spiral vortex groove on turbine, described turbine central shaft there is angular wheel follow the angular wheel on the centripetal end of worm screw to engage each other, angular wheel on the centripetal end of described worm screw is identical with the rotating ratio of turbine with worm screw with the rotating ratio of the angular wheel on turbine central shaft.During described turbine rotation, turbine central shaft drives worm screw to rotate simultaneously, in rotation, turbine and worm screw are opposed embedding running keep the gap between to two ten to be not in contact with each other mutually, described turbine, worm screw is surrounded sealing by housing, the housing of turbine rotation prime direction side, described worm screw outer edge place there is outlet, the convex side body of described turbine inner circle circle centre position leaf there is import, described worm screw can be one, also can be two opposed, can also be multiple in being distributed on the wheel radius surface of turbine to heart shaped, spiral snail on described each worm screw convex with the spiral vortex groove on turbine mutually to embedding coupling, helical-blade on described turbine is convex recessed mutually to embedding coupling with the spiral snail on each worm screw, it keeps the gap between to two ten to be not in contact with each other each other, described turbine central shaft there is angular wheel follow the angular wheel on the centripetal end of each worm screw to engage each other, angular wheel on the centripetal end of described each worm screw is identical with the rotating ratio of turbine with each worm screw with the rotating ratio of the angular wheel on turbine central shaft, during turbine rotation, its central shaft drives each worm screw to rotate simultaneously, in rotation, with each worm screw, turbine remains that the gap between to two ten is not in contact with each other, turbine, each worm screw is surrounded sealing by housing, the housing of turbine rotation prime direction side, described each worm screw outer edge place there is outlet, in described each worm screw two end axles and turbine central shaft has bearing, the convex side body of described turbine inner circle circle centre position leaf there is import, described turbine is when to be that double leaf face is single close centrifugal turbine, its turbine another side the worm screw that is worth on the centrifugal turbine in worm screw merchandiser blade face the same.Bearing is had in described worm screw two end axles He on turbine central shaft.

The beneficial effect of this programme can be learnt according to describing of such scheme, due to the radius of centrifugal turbine wheel face in this scenario having worm screw, spiral snail on described worm screw is convex just in time mates correspondence mutually with the whirlpool groove on turbine, leaf on described turbine is convex corresponding with the recessed mutual coupling of the spiral snail on worm screw, it keeps the gap between to two ten each other, to be not in contact with each other in clearance seal, when turbine rotates, turbine central shaft drives worm screw to rotate simultaneously, the turbine rotated in work and the worm screw of rotation remain that the gap between to two ten is not in contact with each other, turbine and worm screw are all surrounded sealing by housing, fluid enters in the whirlpool groove of turbine by the import on turbine inner circle circle centre position housing, when nose circle in the groove of whirlpool goes to worm position by the convex corresponding shutoff of the snail on rotary worm, along with the rotation of turbine and worm screw, fluid in the groove of whirlpool is extruded by the outside nose circle of interior nose circle by the snail on worm screw is convex, fluid in the groove of whirlpool flows out through outlet, when groove outer nose circle in whirlpool goes to worm position, fluid in the groove of whirlpool is entered in outlet by the convex whirlpool groove that squeezes out of snail, this know-why has part identical with helical-lobe compressor of the prior art, its difference is one: helical-lobe compressor is to complete compression by one or two negative and positive screw rods, this technology follows a worm screw also can be follow multiple worm screw to complete compression by a turbine by a turbine, when a turbine coordinates acting with a worm screw, each whirlpool groove that turbine rotates a circle on turbine wheel face completes first compression.Each whirlpool groove when a turbine coordinates acting with multiple worm screw on turbine wheel face completes and repeatedly compresses, compression increased frequency in same period.Two: make the fluid of turbine inner circle inlet more easily enter in the groove of whirlpool because turbine rotates the centrifugal action produced, also turbo-centrifugal action makes the fluid in the groove of whirlpool not easily flow backwards, and makes compression more smooth.Three: with regard to fluid during same rotational speed turbine inward turning change the line of production raw centrifugal force and worm screw extruding double action under the hydrodynamic pressure that produces than centrifugal compressor of the hydrodynamic pressure that produces higher.The length of the diameter of turbine and spiral vortex groove determines compression exhaust amount and flow and exhaust pressure, and spiral vortex groove is longer, and pressure is higher; Turbine diameter is larger, and flow is larger.As can be seen here, the compression device making medium with fluids such as Oil, Water, Gas that this technology is particularly suitable for that big-flow high-pressure power requires uses, and this technology is compared with prior art, and its beneficial effect implemented is apparent.

accompanying drawing illustrates:

Fig. 1 is the front cross-sectional structural representation of this technology first embodiment.

Fig. 2 is the side, sectional structural representation of this technology first embodiment.

Fig. 3 is the front cross-sectional structural representation of this technology second embodiment.

Fig. 4 is the side, sectional structural representation of this technology second embodiment.

In figure, 1 is housing, and 2 is turbine, and 3 is worm screw, 3 ' is second worm screw, and 4 is that snail is convex, and 4 ' is that snail on second worm screw is convex, 5 is whirlpool groove, and 6 is that leaf is convex, and 7 is that snail is recessed, 7 ' is that snail on second worm screw is recessed, axle centered by 8, the angular wheel centered by 9 on axle, 9 ' is the angular wheel on the centripetal end of worm screw, and 9 〞 are the angular wheel on second centripetal end of worm screw, and 10 is outlet, 10 ' is second outlet, and 11 is import, and 12 is bearing.

embodiment:

For the technical characterstic of this programme more can be clearly demonstrated, below in conjunction with its accompanying drawing, this programme is further elaborated.

Fig. 1, Fig. 2 shows this programme first embodiment, can be found out by accompanying drawing, compressor shown in the present embodiment is primarily of housing 1, turbine 2, worm screw 3 is formed, described turbine 2 is centrifugal turbines that single blade face is closed, described turbine 2 is arranged in housing, on the tapered wheel radius surface being positioned at housing 1 turbine 2 of described worm screw 3, spiral snail convex 4 on described worm screw 3 mates correspondence mutually with the spiral vortex groove 5 on turbine 2, helical-blade on turbine 2 convex 6 mates correspondence mutually with the spiral snail recessed 7 on worm screw 3, it keeps the gap between to two ten to be not in contact with each other in clearance seal shape each other, described turbine 2 central shaft 8 there is angular wheel 9 engage each other with the angular wheel 9 ' on the centripetal end of worm screw 3, angular wheel 9 ' on the centripetal end of described worm screw 3 is identical with the rotating ratio of turbine 2 with worm screw 3 with the rotating ratio of the angular wheel 9 on turbine 2 central shaft 8.Drive worm screw 3 to rotate when turbine 2 central shaft 8 rotates simultaneously, turbine 2 and worm screw 3 relatively rotate and keep the gap between to two ten to be not in contact with each other, turbine 2, worm screw 3 is surrounded sealing by housing 1, the housing 1 rotating prime direction side at worm screw 3 outer edge place turbine 2 there is outlet 10, convex 6 side bodies 1 of described turbine 2 inner circle circle centre position leaf there is import 11, drive worm screw 3 to rotate when described turbine 2 central shaft 8 rotates simultaneously, fluid enters in the whirlpool groove 5 of turbine 2 by the import 11 on turbine 2 inner circle circle centre position housing 1, when nose circle in whirlpool groove 5 goes to worm screw 3 position by the convex 4 corresponding shutoff of the snail on worm screw 3, along with the rotation of turbine 2 and worm screw 3, fluid in whirlpool groove 5 is extruded by the outside nose circle of interior nose circle by the snail on worm screw 3 convex 4, fluid in whirlpool groove 5 is through exporting 10 outflows, when the outer nose circle of whirlpool groove 5 goes to worm screw 3 position, fluid in whirlpool groove 5 is entirely squeezed out whirlpool groove 5 by snail convex 4 and enters in outlet 10, bearing 12 is had in described worm screw 3 two end axles He on turbine 2 central shaft 8.

Fig. 3, Fig. 4 shows this programme second embodiment, can be found out by accompanying drawing, compressor shown in the present embodiment is primarily of housing 1, turbine 2, worm screw 3 and second worm screw 3 ' are formed, described turbine 2 is centrifugal turbines that single blade face is closed, described turbine 2 is arranged in housing, one of them worm screw 3 described is tapered to be positioned on the upper semi-circle wheel radius surface of housing 1 turbine 2, described second worm screw 3 ' is positioned on the lower semi-circle wheel radius surface of housing 1 turbine 2 in inverted cone, spiral snail convex 4 on described worm screw 3 is mutual to embedding coupling with the spiral vortex groove 5 on turbine 2, helical-blade on turbine 2 convex 6 is mutual to embedding coupling with the spiral snail recessed 7 on worm screw 3, spiral snail convex 4 ' on described second worm screw 3 ' is mutual to embedding coupling with the spiral vortex groove 5 on turbine 2, helical-blade convex 6 on described turbine 2 is mutual to embedding coupling with the spiral snail recessed 7 ' on second worm screw 3 ', it keeps the gap between to two ten to be not in contact with each other each other and is clearance seal shape, described turbine 2 central shaft 8 there is angular wheel 9 engage each other with the angular wheel 9 ' on the centripetal end of worm screw 3 and angular wheel 9 〞 on second centripetal end of worm screw 3 ', angular wheel 9 ' on the centripetal end of described worm screw 3 is identical with the rotating ratio of turbine 2 with second worm screw 3 ' with worm screw 3 with the rotating ratio of the angular wheel 9 on turbine 2 central shaft 8 with angular wheel 9 〞 on second centripetal end of worm screw 3 '.When turbine 2 rotates, its central shaft 8 drives worm screw 3 and second worm screw 3 ' to rotate simultaneously, turbine 2 is not in contact with each other with the gap between worm screw 3 and second worm screw 3 ' keep to two ten, turbine 2, worm screw 3, second worm screw 3 ' is surrounded sealing by housing 1, the housing 1 that described worm screw 3 outer edge place turbine 2 rotates prime direction side there is outlet 10, the housing 1 that described second worm screw 3 ' outer edge place turbine 2 rotates prime direction side there is second to export 10 ', convex 6 side bodies 1 of described turbine 2 inner circle circle centre position leaf there is import 11, described turbine 2 central shaft 8 drives worm screw 3 and second worm screw 3 ' to rotate simultaneously when rotating, fluid enters in the whirlpool groove 5 of turbine 2 by the import 11 on turbine 2 inner circle circle centre position housing 1, when nose circle in whirlpool groove 5 goes to worm screw 3 and second worm screw 3 ' position by the snail on worm screw 3 convex 4 and and second worm screw 3 ' on the corresponding shutoff of snail convex 4 ', along with turbine 2, the rotation of worm screw 3 and second worm screw 3 ', fluid in whirlpool groove 5 is extruded by the outside nose circle of interior nose circle by the snail convex 4 ' on the snail on worm screw 3 convex 4 and second worm screw 3 ', fluid in whirlpool groove 5 is through exporting 10 and second outlet 10 ' outflow, when the outer nose circle of whirlpool groove 5 goes to worm screw 3 and second worm screw 3 ' position, fluid in whirlpool groove 5 is entirely squeezed out whirlpool groove 5 by the snail convex 4 ' on the snail on worm screw 3 convex 4 and second worm screw 3 ' and enters in outlet 10 and second outlet 10 ', in described worm screw 3 and second worm screw 3 ' two end axles and turbine 2 central shaft 8 has bearing 12.

beneficial effect

Can be found out by describing of above-mentioned two embodiments, the working principle of this technology is substantially identical with helical-lobe compressor working principle of the prior art, the advantage of this technology is one: this technology can be with a worm screw pairing work by a turbine, also can be carried out compression work by a turbine with multiple worm screw pairing, when a turbine is with a worm screw pairing work, each whirlpool groove that turbine often rotates a circle on turbine wheel face completes first compression, when a turbine is with two worm screw pairing work, each whirlpool groove on turbine wheel face respectively completes twice compression work, that is, when a turbine is with multiple worm screw pairing work, each whirlpool groove on turbine wheel face respectively completes repeatedly compression work, namely in same rotating speed whirlpool groove to complete the number of times of compression work more than helical-lobe compressor of the prior art.Two: make the fluid in turbine inner circle housing upper inlet more easily enter in the groove of whirlpool because turbine rotates the centrifugal action produced, also turbo-centrifugal action makes the rate of flow of fluid in the groove of whirlpool accelerate and not easily flow backwards, and makes compression work more smooth.Three: during same rotational speed fluid turbine inward turning change the line of production raw centrifugal force and worm screw extruding double action under the hydrodynamic pressure that produces than simple centrifugal compressor of the hydrodynamic pressure that produces higher, be more suitable for the work of calming the anger of high-speed large-flow.As can be seen here, this technology is compared with prior art, and its beneficial effect implemented is apparent.

Claims (3)

1. a new type of compression device, primarily of housing, turbine, worm screw is formed, it is characterized in that: described turbine is that centrifugal turbine is arranged in housing, described worm screw is tapered to be positioned on the wheel radius surface of housing turbine, spiral snail on described worm screw convex with the whirlpool groove on turbine mutually to embedding coupling, helical-blade on described turbine is convex recessed mutually to embedding coupling with the spiral snail on worm screw, it keeps certain interval to be not in contact with each other each other, the central shaft of described turbine there is angular wheel follow the angular wheel on the centripetal end of worm screw to engage each other, angular wheel on the centripetal end of described worm screw is identical with the rotating ratio of turbine with worm screw with the rotating ratio of the angular wheel on turbine central shaft, described turbine, worm screw is surrounded sealing by housing, the housing of turbine rotation prime direction side, described worm screw outer edge place there is outlet, the convex side body of described turbine inner circle circle centre position leaf there is import, bearing is had in described worm screw two end axles He on turbine central shaft.

2. a kind of new type of compression device according to claim 1, it is characterized in that: described turbine wheel face has two worm screws, one of them worm screw is tapered to be positioned on the upper semi-circle wheel radius surface of housing turbine, second worm screw is that inverted cone is positioned on the lower semi-circle wheel radius surface of housing turbine, spiral snail on described worm screw convex with the spiral vortex groove on turbine mutually to embedding coupling, helical-blade on described turbine is convex recessed mutually to embedding coupling with the spiral snail on worm screw, spiral snail on described second worm screw convex with the spiral vortex groove on turbine mutually to embedding coupling, helical-blade on described turbine is convex follows the spiral snail on second worm screw recessed mutually to embedding coupling, it keeps certain interval to be not in contact with each other in clearance seal shape each other, described turbine central shaft there is angular wheel follow the angular wheel on the angular wheel on the centripetal end of worm screw and second centripetal end of worm screw to engage each other, angular wheel on the centripetal end of described worm screw is identical with the rotating ratio of turbine with second worm screw with worm screw with the rotating ratio of the angular wheel on turbine central shaft with the angular wheel on second centripetal end of worm screw, turbine, worm screw, second worm screw is surrounded sealing by housing, the housing of turbine rotation prime direction side, described worm screw outer edge place there is outlet, the housing of turbine rotation prime direction side, described second worm screw outer edge place there is second outlet, the convex side body of described turbine inner circle circle centre position leaf there is import, in described worm screw and second worm screw two end axles and turbine central shaft has bearing.

3. a kind of new type of compression device according to claim 1, it is characterized in that: described turbine wheel face has multiple worm screw, described multiple worm screw is tapered to be centripetally distributed on the wheel radius surface of turbine in housing, spiral snail on described each worm screw convex with the spiral vortex groove on turbine mutually to embedding coupling, helical-blade on described turbine is convex recessed mutually to embedding coupling with the spiral snail on each worm screw, it keeps certain interval to be not in contact with each other each other, described turbine central shaft there is angular wheel follow the angular wheel on the centripetal end of each worm screw to engage each other, angular wheel on the centripetal end of described each worm screw is identical with the rotating ratio of turbine with each worm screw with the rotating ratio of the angular wheel on turbine central shaft, turbine, each worm screw is surrounded sealing by housing, the housing of turbine rotation prime direction side, described each worm screw outer edge place there is outlet, the convex side body of described turbine inner circle circle centre position leaf there is import, in described each worm screw and two end axles and turbine central shaft has bearing.