WO2010130146A1

WO2010130146A1 - Multifunctional synchronous backflow ventilating compressor

Info

Publication number: WO2010130146A1
Application number: PCT/CN2010/000651
Authority: WO
Inventors: 林钧浩
Original assignee: Lin Junhao
Priority date: 2009-05-15
Filing date: 2010-05-10
Publication date: 2010-11-18
Also published as: CN101566164A

Abstract

A multifunctional synchronous backflow ventilating compressor comprises a shell (1), an air inlet (2) of the shell, an air outlet (3) of the shell, an impeller (4), impeller blades (5), an airflow channel (15) inside the impeller and an impeller shroud (7). The axial front sides of the impeller blades (5) gradually axially tilt along the radial direction of the impeller from front to back towards the axial direction of the impeller; the axial back sides of the impeller blades (5) gradually axially tilt along the radial direction of the impeller from front to back towards the axial direction of the impeller; the axial front side of the impeller (4) gradually axially tilts along the radial direction of the impeller from front to back towards the axial direction of the impeller; the axial direction back side of the impeller (4) gradually axially tilts along the radial direction of the impeller from front to back towards the axial direction of the impeller; and the airflow channel (15) inside the impeller gradually axially tilts along the radial direction of the impeller from front to back towards the axial direction of the impeller. The part of the axial back side of the impeller gradually axially tilting along the radial direction of the impeller from front to back towards the axial direction of the impeller is provided with the impeller shroud (7) in the form of a conical sleeve. The ventilating compressor of the present invention has the advantages of simple structure, small volume, light weight, convenient transportation and mounting, good pressurized effect, high efficiency, low noise and the like.

Description

Multifunctional synchronous backflow ventilation compressor

The invention relates to the field of air purification compression technology, in particular to a multifunctional synchronous backflow ventilation compressor. Background technique

Nowadays, various ventilators, compressors, gas compressors, etc., have poor pressurization effects and low mechanical efficiency, which are neither energy-saving nor environmentally friendly. Disclosure of invention

SUMMARY OF THE INVENTION An object of the present invention is to overcome the above-mentioned shortcomings of the prior art and to provide a multi-functional synchronous after-circulating air compressor capable of high efficiency, energy saving, and low noise of various ventilators, compressors, and gas compressors.

The object of the present invention can be achieved by the following technical measures: a multi-functional synchronous backflow ventilation compressor, including an organic shell, a casing air inlet, a casing air outlet, an impeller, an impeller blade, an impeller inner air flow passage, an impeller vane, The utility model is characterized in that the axial front side of the impeller blade is gradually inclined axially from the front to the rear of the impeller toward the axial direction of the impeller, and the axial rear side of the impeller blade is gradually inclined axially from the front to the rear of the impeller toward the axial direction of the impeller. The front side is gradually inclined axially from the front to the rear of the impeller toward the axial direction of the impeller. The axial rear side of the impeller is gradually inclined axially from the front to the rear of the impeller toward the axial direction of the impeller. The inner airflow passage of the impeller gradually follows the radial direction of the impeller. Axial tilting.

In order to further achieve the object of the present invention, the impeller axial rear side is provided with an impeller axial air outlet in the radial direction of the impeller from the front to the rear toward the axially inclined portion of the impeller.

In order to further achieve the object of the present invention, the axial rear side of the impeller has no impeller blade disc in the radial direction of the impeller from the front to the rear toward the axial direction of the impeller.

In order to further achieve the object of the present invention, the radial end of the impeller is provided with an impeller radial air outlet.

In order to further achieve the object of the present invention, the air inlet of the casing is provided with a diffusion splitter in the form of an expanded structure from the front to the rear, and the diffusion deflector is provided with a connecting deflector, and the diffusion splitter is connected with the deflector. The shell inlet side wall is connected. In order to further achieve the object of the present invention, the axial side of the impeller is provided with a drainage diffuser in the form of an expanded structure from the front to the rear, and the drainage diffuser is connected to the impeller.

Multi-functional synchronous rear-flow ventilation compressor, the casing comprises a spiral casing, a cylindrical casing, a conical tubular casing, a cylindrical casing, a volute casing, and a conical cylindrical volute A variety of structural forms such as a combined casing. The impeller includes a rear-flow fan impeller (multi-wall blade structure), a synchronous rear-flow fan impeller (synchronous diversion supercharger blade structure) and a general-purpose old centrifugal fan impeller. The impeller blades are multi-walled blades (including a negative-pressure partition wall and Thrust wall), with synchronous pilot supercharger blades (synchronous diversion booster including semi-span and full span) and single-wall impeller blades (ie old centrifugal fan impeller blades).

For the convenience of description and accurate expression, several related words are explained here:

The side or side wall of the impeller to which the central axis of the impeller is directed, the side or side wall of the casing is referred to as an axial side or an axial side wall;

The impeller and the air inlet side of the machine body are the axial front side, and the corresponding one side is the axial rear side, and the axial front and the axial rear reference and the like;

Near the impeller axis is the radial front of the impeller, the front end is the radial front end of the impeller, near the outer circumference of the impeller is the radial rear of the impeller, and the outer edge is the radial end of the impeller.

According to the present invention, the axial front side of the impeller blade is gradually axially inclined from the front to the rear in the radial direction of the impeller toward the axial direction of the impeller, and the axial rear side of the impeller blade is gradually inclined axially from the front to the rear toward the axial direction of the impeller. That is to say, the axial front side and the axial rear side of the impeller blades can each be individually axially inclined from the front and the rear toward the axial direction of the impeller (or the axial front or the axial rear) in the radial direction of the impeller, respectively. The lateral and axial rear sides may be the same in the radial direction of the impeller from the front to the rear, and may be reversed, and the inclination angles may be equal and may be unequal. The same is true for the inner side air flow passage of the impeller, the axial front side of the front side, and the axial rear side of the front side of the impeller.

If the axial front side of the impeller blade is gradually axially inclined from the front to the rear of the impeller toward the axial direction of the impeller, and the axial rear side of the impeller blade is gradually axially inclined from the front to the rear of the impeller toward the axial rear of the impeller, the impeller blade The axially expanding and widening structure is formed from the front side to the rear side of the impeller in the radial direction of the impeller; if the axial front side and the axial rear side of the impeller are gradually inclined from the front to the rear in the radial direction of the impeller, the impeller vane shaft The axial length of the axially inclined portion is equal to each other; if the axial front side and the axial rear side of the impeller blade are gradually inclined from the front to the rear in the radial direction of the impeller, the axial inclination angles are not equal, The axial length of the axially inclined portion of the impeller blade is not equal; the inner airflow passage formed by the impeller is also formed in the axial direction of the impeller in the axial direction of the impeller. The axial expansion angles may also be equal or unequal, and the radial lengths of the axially inclined portions on both sides of the axial direction may be equal or unequal. The impeller of this structure is also axially expanded and widened from the front and the rear of the impeller in the radial direction of the impeller toward the axial forward and axial rear of the impeller, respectively, and the angle of expansion and widening is equal. , can not be equal.

If the axial front side of the impeller blade is gradually axially inclined from the front to the rear of the impeller toward the axial rear of the impeller, and the axial rear side of the impeller blade is gradually axially inclined from the front to the rear of the impeller toward the axial direction of the impeller, the impeller The blade is formed in such a manner that its axial sides are gradually inclined and narrowed from the front to the rear in the radial direction of the impeller. If the axial inclination angles of the impeller blades are gradually equal, the radial lengths of the axially inclined portions of the impeller blades are equal. If the inclination angles are not equal, the axially inclined portions of the axial directions of the impeller blades are gradually inclined. The lengths are not equal. The corresponding inner airflow passage of the impeller is also the same on both sides of the axial direction and the axial sides of the impeller.

If the axial front side of the impeller blade is gradually axially inclined from the front to the rear of the impeller in the radial direction of the impeller, the axial rear side of the impeller blade is gradually inclined axially from the front to the rear of the impeller in the radial direction of the impeller, when the impeller vane shaft When the gradual axial inclination angle of the forward side is greater than the gradual axial inclination angle of the axial rear side of the impeller blade, the impeller blade is gradually expanded and widened from the front to the rear along the radial direction of the impeller, and the axial direction of the impeller blade is gradually axially forward. When the inclination angle is smaller than the axial inclination angle of the axial rear side of the impeller blade, the impeller blade is gradually reduced in axial direction from the front to the rear in the radial direction of the impeller, and the axial direction of the front side of the impeller blade is gradually inclined. When the angles are equal, the impeller blades are in the same cross-sectional configuration along the radial direction of the impeller from the front to the rear. Correspondingly, the axial sides of the inner flow passage of the impeller and the axial sides of the impeller will also form several corresponding structural forms (the impeller is in the form of a conical cylinder with the expanded end facing the impeller toward the front).

If the axial front side of the impeller is gradually inclined axially from the front to the rear of the impeller toward the axial rear of the impeller, the axial rear side of the impeller blade is gradually inclined axially along the impeller in the radial direction of the impeller from the front to the rear toward the axial rear of the impeller, when the impeller blade The axial axial inclination angle of the axial front side is greater than the axial axial inclination angle of the rear side of the impeller, and the impeller blades are formed into a gradually axially narrowing structure from the front to the rear in the radial direction of the impeller; The axial inclination angle is smaller than the axial inclination angle of the axial rear side of the impeller blade, and the impeller blade is gradually expanded axially from the front to the rear in the radial direction of the impeller; when the impeller blade is axially forward, the axial rear side is gradually inclined. When the angle of inclination is equal, the impeller blades are The radial direction along the impeller is the same as the width of the front and rear widths; the corresponding axial sides of the airflow passage on the inner side of the impeller, and the axial sides of the impeller will also form several corresponding structural forms (the impeller is the expansion end orientation) The impeller is oriented toward the front of the cone structure).

According to the present invention, regardless of the structural form of the impeller, an impeller radial end air outlet may be provided at a radial end thereof (referred to as an impeller radial air outlet, the outlet direction may be radial, and may be radial axial inclination of). If the axial front side and the axial rear side of the impeller are gradually axially inclined from the front to the rear of the impeller in the axial direction of the impeller, the impeller radial outlet end of the impeller is formed toward the axial rear of the impeller. The axial radial direction is inclined, and the impeller radial outlet outlet direction can be designed to be either inclined to the axial direction or to the radial direction; or to the axial direction, to facilitate several impellers. (Either the old centrifugal fan impeller, or the rear-flow fan impeller or the synchronous rear-flow fan impeller are applicable). The high-pressure blower and the high-pressure extra-high pressure compressor are used in series.

According to the present invention, regardless of the structural form of the axial rear side of the impeller, an axial air outlet of the impeller may be disposed on the axial side, wherein the axial side faces the impeller axially forward or axially rearward and backward in the radial direction of the impeller Gradually axially inclined structure makes it easier to set the impeller axial air outlet. The impeller is designed to be gradually inclined from the axial rear side in the radial direction of the impeller from the front to the rear toward the front or the rear of the impeller shaft. The axial rear side of the impeller is axially forward and rearward of the impeller in the radial direction of the impeller. The entire axially inclined portion to the rear can be an axial air outlet of the impeller, that is, almost all of the axial side surfaces of the impeller can discharge gaseous substances to the outside. The rear-flow fan impeller and the synchronous rear-flow fan impeller can originally discharge the gaseous substance axially from the radial end outlet of the impeller, and if the axial rear side of the impeller is further designed to be axially rearward or axially rearward and backward of the impeller. The axially inclined structure in front is gradually more effective in discharging the gaseous substances in the axial direction.

The axial rear side of the impeller is gradually inclined axially from the front to the rear of the impeller toward the axial forward or axial rear of the impeller. The axially inclined portion of the axial rear side of the impeller may be provided with an impeller blade disc (conical cylinder structure, the circle The expansion end of the cone-shaped impeller blade disk may be directed toward the axial direction of the impeller or toward the axial rear of the impeller. The impeller vane negative pressure isolation wall may be provided, and the synchronous diversion booster may be provided, or the impeller vane may not be provided. Impeller blade negative pressure isolation wall or synchronous flow supercharger. The axial rear side of the impeller may be provided with an impeller blade disc throughout the gradually axially inclined portion, or both impeller blade discs, impeller vane negative pressure partition walls or synchronous diversion superchargers, or impeller blades Negative pressure isolation wall or synchronous flow supercharger; the structure, the impeller axial rear side of the entire gradually axially inclined portion does not have an impeller The axial air outlet is provided with an impeller radial air outlet at the radial end of the impeller. The axial rear side of the impeller may be provided with an impeller blade disc in a part of the gradually axially inclined portion, or an impeller blade disc and a negative pressure dividing wall or a synchronous diversion supercharger, or a single impeller negative pressure partition wall or a synchronous guide. The flow supercharger; the structural form of the impeller axial rear side, the impeller axial air outlet can be arranged in the gradually axially inclined portion without the impeller vane, the impeller vane negative pressure partition wall or the synchronous flow supercharger . The axial rear side of the impeller may have no impeller vane in the entire gradually axially inclined portion, and no impeller vane negative pressure partition wall or synchronous diversion booster; the structural form, the impeller axial rear side, may be The axially inclined portions of the impeller are provided with axial air outlets.

When the axial side of the impeller forms a conical cylinder structure with the expansion end facing the axial direction of the impeller, and the impeller blade disc of the conical cylinder shape is further provided, the impeller blade disc in the shape of the disc of the conical cylinder shape is arranged. The disc-shaped impeller blade disc supports the side wall of the cone wheel of the cone cylinder to ensure that the entire impeller is not twisted and deformed, thereby ensuring stable operation of the impeller and stable performance of the fan.

Regardless of the structural form of the impeller, the invention can simultaneously provide an axial air outlet of the impeller on the rear side of the impeller and a radial air outlet of the impeller at the radial end of the impeller; The radial air outlet can promote the impeller to have a better suction and discharge effect.

The impeller of the invention (including the rear flow fan impeller, the synchronous rear flow fan impeller, the general old centrifugal fan impeller) has the above various different structural forms, and can set the impeller radial air outlet and the impeller axial air outlet. At the same time, both the impeller radial air outlet and the impeller axial air outlet can be provided, which can be used for a variety of different requirements of the fan. If the axial front side of the impeller is axially forward and backward along the impeller The structure is gradually inclined toward the front of the impeller shaft or toward the axial rear of the impeller, or the axial rear side of the impeller is separately formed in the radial direction of the impeller from the front to the rear toward the axial forward or axial rear of the impeller. The impellers of the several structural forms are suitable for use in several series assembly into a high pressure blower and a high pressure ultra high pressure compressor compressor. Because the impeller of the invention is axially rear exhausted, the fan, the compressor and the gas compressor assembled by the impeller have many functions and wide applications, so it is named as a multi-functional synchronous backflow ventilation compressor.

The multi-functional synchronous rear-flow ventilation compressor, wherein the axial rear side of the impeller is gradually inclined axially from the front to the rear of the impeller toward the axial rear of the impeller, and the axial rear side of the impeller is axially forward and backward along the impeller radial direction toward the impeller The axial rear is gradually inclined axially. The two structural forms (the axial side of the impeller are both in the form of a conical cylinder with the expanding end facing the axial rear of the impeller), especially suitable for multi-stage series assembly of impellers into high-pressure ventilators, high-pressure UHV Gas and gas compressors are used. Impeller diameter of the structure The direction of the outlet of the air outlet is inclined in the axial direction of the axial direction, and the axial direction of the axial direction of the axial direction of the impeller is better. The inner flow passage of the impeller in the structural form is gradually axially inclined from the front to the rear in the radial direction of the impeller (or substantially axial direction). In this way, the airflow enters the impeller axially from the air inlet of the fan, and then flows through the inner airflow passage of the impeller in the axially oblique direction of the axial direction, and then flows out of the impeller axially from the axial side of the axial direction of the impeller. The airflow does not change from axial to radial commutation in the wind turbine body, but basically flows in one direction along the axial direction of the impeller. This technology is called the downstream pressurized rear-end technology.

The two types of impellers can be used in series to make centrifugal or centrifugal axial high pressure UHV blowers, compressors, and gas compressors. The gas sucked in the axial direction of one impeller is processed and then axially discharged to the other impeller, and the other impeller is axially sucked again, and then processed and then axially discharged to the other impeller... Any static diversion facility can ensure that several impellers in multiple stages are working properly to process the required high-pressure extra-high pressure airflow.

The use of the impeller in the form of an axial exhaust structure in series to form a high pressure blower, a compressor, and a gas compressor has the following advantages:

1. Since the impeller is centrifugal, the axial front and rear axial sides of the impeller are gradually inclined axially from the front to the rear toward the axial rear of the impeller, and the inner airflow passage of the impeller is gradually inclined axially. The airflow enters the impeller axially and then flows axially through the impeller and out of the impeller. During the working process, the airflow flows substantially along the axial direction in one direction, so that the airflow in the airflow passage inside the impeller can not only laterally overflow the impeller, but also the negative pressure formed by the high-speed flow can fully absorb the external shield. Therefore, the entire front axial side of the impeller of this type of structure (without the impeller blade disc or the small impeller blade disc) can almost completely suck the gaseous substance, and in addition, it is centrifugal, so the impeller has a large flow rate. The boosting effect is good.

2. Since the inner airflow passage of the impeller is gradually inclined from the axial direction of the impeller to the axial direction, the airflow flowing through the outflow impeller is basically axially unidirectional (not less than 90°). ()), the entire impeller axial front side (no or a small front disc), due to the negative pressure gap or synchronous downstream air inlet or blade clearance (old centrifugal fan impeller blade clearance), the entire axis of the impeller The outward suction of gaseous material on the front side is omnipotent. The front axial side of the impeller can be used to vent the airflow backwards from the previous impeller, whether it is oblique or lateral, whether it is DC or rotating. Directly pumping it directly, without using a static flow guiding device to guide the airflow to the air inlet of the impeller (even if the intermediate flow guiding device is required, the flow path bends and bends is small). 3. The airflow is axially inclined from the middle of the front part of the radial direction of the first stage impeller to the radial end of the final stage impeller, and enters the final stage impeller from the radial end inlet of the final stage impeller, and then the final impeller diameter The final stage impeller is discharged to the end outlet. The first stage after the first stage of the impeller has a large centrifugal force at the radial end and a large centrifugal force for the airflow. Therefore, when the airflow is discharged from the end outlet of the rotor at the end of the rotor, its volume will be much smaller than that of the first-stage impeller inlet, and it can be reduced by several times several hundred times several hundred times... and its pressure can be increased several times. Ten times hundreds of times...

4. There is a certain axial spacing space between the two impellers. The spacing space is larger than the airflow passage volume inside the impeller, which can fully decelerate and expand the high-speed airflow discharged from the axial air outlet of the axial direction of the front impeller. The size of the space should be appropriately set according to actual needs. That is to say, the high-speed airflow after the processing of the previous impeller can be sufficiently decelerated and expanded without the need to specially set the deceleration and expansion facilities between the two impellers.

5. Because the impeller is directly axially discharged from the airflow, it is directly axially sucked. During the processing, if it is necessary to cool down the high-pressure and high-temperature gas in the process, a cooling and cooling facility can be directly installed between the impellers. The high-pressure high-temperature airflow after the previous impeller is processed is directly axially discharged to the latter impeller to continue to work.

6. The axial rear side and the axial front side of the impeller are gradually inclined axially from the front to the rear of the impeller in the radial direction of the impeller. The front side of the impeller is axially, and the impeller blade can be added to the middle portion thereof to make the diameter. The gas substance is axially sucked toward the radial rear portion of the middle portion, and the impeller blade disc is added radially in the radial middle portion of the middle portion, and a special air inlet port at the middle of the impeller is added at the middle portion thereof, so that the axial direction of the impeller is dedicated. Aspirate foreign matter. The airflow enters the impeller axially from the axial front side of the front side of the impeller, and then axially exits the impeller. The air flow passage bends less and has less friction loss, so the rotor consumes less energy and has higher efficiency. The airflow enters the impeller axially from the front special axial air inlet of the axial side of the impeller, and flows axially through the axial direction. Then, the axial direction of the impeller is axially discharged from the rear side of the impeller (near the radial end of the impeller). The radial flow of the airflow is large, and the single-stage impeller has a good pressurization effect, because the number of impellers in series can be reduced, and the axial dimension of the rotor can be shortened.

7. Since the impeller is directly axially pumped to the airflow, it is directly axially discharged. If a static diversion facility is required between the two impellers in the airflow passage inside the casing, the structure can be very simple. , such as the wind deflector, only a cone-shaped structure, the expansion end of which is connected to the inner side of the front impeller and connected to the inner side wall of the casing, receiving the airflow from the axial rear side of the previous impeller; The contraction end faces the rear axial side of the impeller, and the wind deflector receives the gas from the previous impeller The flow guiding flow is in front of the impeller front axial side impeller inlet (impeller negative pressure gap, synchronous downstream air inlet, special air inlet in the middle of the impeller), and the wind deflecting contraction end outlet can be guided to the latter impeller as needed Any desired part of the front axial side, such as the radial rear end, the radial rear rear, the radial rear, the radial middle, the radial front, the special air inlet in the middle of the impeller.

In short, the axial side of the impeller is gradually inclined axially from the front to the rear toward the axial rear of the impeller in the radial direction of the impeller. The axial side and the front axial side of the impeller are axially oriented from the front to the rear toward the axial rear of the impeller. Tilting, high-pressure blowers, compressors, gas compressors composed of impellers of the two structural forms (the axial side of the impeller is a conical tube structure with the expansion end facing the axial rear of the impeller), the entire working process, the air flow bend With fewer turns, shorter processes and less friction loss, they have a better boosting effect, higher efficiency, energy saving and low noise.

The casing of the present invention may be in the form of a cylindrical cylinder structure, which may be a cylindrical combination of cylindrical cylinders, may be a cylindrical cylindrical conical cylinder combination, may be in the form of a volute structure, and may be in the form of a variant volute structure. The variant volute structure, that is, the volute conical cylinder hybrid type, the inner flow passage of the casing on the inner side of the casing is inclined toward the axial rear side of the axial direction and the inner side of the same cone-shaped impeller The flow direction of the air flow channel is constant. When working, the eddy current is small, the friction loss is small, the energy is more efficient, and the noise is lower.

Multifunctional synchronous backflow ventilation of the present invention compared to a universal axial flow fan (including an old diagonal flow, mixed flow fan) and an old centrifugal compressor gas compressor, an old axial flow compressor gas compressor Compressor structure is simple, small in size, less in material consumption, light in weight, convenient in handling and transportation, saving resources, good supercharging effect, high efficiency, energy saving, low noise, and environmental protection.

The invention is suitable for being assembled into a centrifugal fan blower and an axial fan blower, and is also suitable for being assembled into a centrifugal compressor gas compressor and an axial compressor gas compressor.

The air inlet of the casing of the invention can also be provided with a diffusing splitter in the form of an expanded structure from the front to the rear (the air inlet of the casing, the diffusing splitter, the air inlet end is the front end, and the air outlet end is the rear end), and the diffusion splitter A connecting baffle is arranged on the upper side, and the diffusing shunt is connected with the side wall of the air inlet of the casing through the connecting baffle.

The casing mentioned here refers to a centrifugal fan casing with a spiral shape, a cylindrical cylindrical conical tubular combination, a conical volute combination, a volute shape, etc.; the so-called casing air inlet refers to the centrifugal fan air inlet. The so-called air inlet of the casing refers to the outer side of the air inlet of the casing, the inside and outside of the air inlet of the casing, and the inner side of the air inlet of the casing. That is to say, the diffusion splitter can be arranged directly on the outer side of the outlet end of the air inlet of the casing and close to the air inlet of the casing, and can be arranged inside and outside the outlet of the casing inlet, and can be arranged in the casing. Inside the air inlet.

The diffusing splitter may be in the form of a tapered structure, which may be a spherical crown, a spherical shape, or the like, which can uniformly spread the distributed airflow. The function of the diffuser is to divert the gas material passing through the air inlet of the casing to the inner airflow passage of each impeller of the impeller, so as to avoid the airflow from the air inlet of the casing impinging on the impeller vertically. The formation of intense eddy currents can improve efficiency and reduce noise. Secondly, the material passing through the air inlet of the casing is uniformly diffused and divergent in the axial direction to the radial end of the impeller (the radial front portion near the axial center of the impeller, and the radial rear portion of the impeller near the outer circumference of the impeller, outside the impeller) The rounded edge is the radial end), which avoids the gas, liquid and solid matter passing through the air inlet of the casing to enter the inside of the impeller, and can avoid the occurrence of intense eddy current, thereby improving efficiency and reducing noise.

The air inlet of the casing mentioned here may be in the form of a cylindrical tube structure, and may be a structure form that expands from front to back, wherein the expanded structure is the best, because the side wall of the air inlet of the casing in the form of an expanded structure is expanded from front to back. The axially-inclined airflow passage formed between the diffusing splitters is more favorable for the axially inclined diffusion flow state of the airflow in the air inlet of the casing.

According to the present invention, a drainage diffuser which is expanded from the front to the rear may be provided on the axially outer side of the impeller. The axial outer side of the impeller here refers to the impeller vane, the impeller vane negative pressure partition wall, the synchronous diversion booster, the impeller vane axial edge, the impeller intermediate dedicated air inlet, and the axial outer side of the impeller. That is to say, the drainage diffuser can be arranged on the axial side wall of the impeller (including the impeller blade disc, the axial edge of the impeller blade, etc.), and can be arranged in the special air inlet of the impeller, and can be arranged in the axially outer side of the impeller.

The axial rear end of the impeller drainage diffuser is connected to the impeller. This connection is available in both direct and indirect connections. The direct connection is that the rear end of the drainage diffuser is directly connected to the impeller; the intermediate connection is that the rear end of the drainage diffuser is provided with a drain connector, and the drainage diffuser is connected to the impeller by means of a drain connector.

The drainage diffuser is expanded from front to back (the inlet of the drainage diffuser is the front end of the drainage diffuser, and the outlet end is the rear end of the drainage diffuser), and the expansion range can be arbitrarily expanded between 0° and 180°. The large expansion angle can be determined according to actual needs. The drainage diffuser can be used in a variety of expanded structures, such as a conical tubular shape, a conical shape, a spherical crown shape, a spherical shape, and the like, which can uniformly diffuse the distributed airflow.

The function of the drainage diffuser is the same as that of the diffusion diverter. The airflow coming from the axial direction changes to the axial radial tilt direction, and the diffusion distributes to the inner airflow passage of each impeller of the impeller to avoid the large eddy current loss caused by the intense eddy current, thereby improving the efficiency and reducing the noise. Secondly, the gas, liquid and solid matter sent from the air inlet of the casing are uniformly diffused and distributed to the radial end of the impeller in a radial direction, so as to prevent various substances coming in from the air inlet of the casing from contacting the impeller or entering the inner side of the impeller, and It also avoids the creation of intense eddy currents, which increases efficiency and reduces noise.

The invention will be explained in detail below with reference to the accompanying drawings and embodiments. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic view showing the structure of a first embodiment of the present invention;

Figure 2 - Schematic diagram of the front axial side structure of the impeller according to the first embodiment of the present invention;

Figure 3 - Schematic diagram of the axial side structure of the impeller according to the first embodiment of the present invention;

Figure 4 - Schematic diagram of the second embodiment of the present invention;

Figure 5 - Schematic diagram of the structure of the impeller of the second embodiment of the present invention;

Figure 6 - Schematic diagram of the third embodiment of the present invention;

Figure 7 - Schematic diagram of the fourth embodiment of the present invention;

Figure 8 - Schematic diagram of the fifth embodiment of the present invention;

Figure 9 is a schematic view showing the structure of an impeller according to a fifth embodiment of the present invention;

Figure 10 is a schematic view showing the structure of a sixth embodiment of the present invention;

Figure 11 - Schematic diagram of the seventh embodiment of the present invention;

Figure 12 - Schematic diagram of the eighth embodiment of the present invention;

Figure 13 - Schematic diagram of the structure of the ninth embodiment of the present invention;

Figure 14 is a schematic view showing the structure of a tenth embodiment of the present invention;

Figure 15 is a schematic view showing the structure of an eleventh embodiment of the present invention.

Description of the drawings: 1 casing, 2 casing air inlet, 3 casing air outlet, 4 impeller, 5 impeller blades, 6 synchronous diversion booster, 7 impeller vane, 8 impeller axial air outlet, 9 Synchronous downstream air inlet, 10 casing axial outlet deflector, 11 wind deflector, 12 reinforcement lacing, 13 impeller intermediate air inlet, 14 impeller radial air outlet, 15 impeller inner air passage, 16 motor (motor), 17 wind deflector outlet, 18 coupling, 19 rotor axial diffuser, 20 diffuser, 21 connecting baffle, 22 thrust wall, 23 negative pressure barrier, 24 negative pressure clearance , ²⁵ casing axial rear side air inlet Port, 26 drain diffuser, 27 drain connector, 28 drive shaft. The best way to implement the invention

Embodiment 1 (refer to FIG. 1, FIG. 2, FIG. 3), a multi-functional synchronous rear-flow ventilation compressor, including a casing in the form of a cylindrical cylinder, an air inlet of the casing 2, an air outlet of the casing 3, and a synchronous flow increase The impeller 4 formed by the impeller blades of the compressor, the impeller blades 5 (with the semi-span synchronous superconductor 6), the impeller vanes 7, the axial rear side of the impeller blades 5 and the axial front side are all along the radial direction of the impeller From the front to the rear, the axial direction of the impeller is gradually inclined. The axial direction of the rear side of the impeller is gradually inclined axially from the front to the rear of the impeller in the radial direction of the impeller. To the inclined structure form. The axial rear side of the impeller is inclined from the front to the rear toward the axial rearward of the impeller in the radial direction of the impeller, and the axial direction of the front side of the impeller is inclined toward the axial direction of the impeller. The impeller vane 5 is formed from the front to the rear in the radial direction of the impeller. Gradually axial expansion expands the structure. The axial side surface of the impeller is gradually inclined axially from the front to the rear of the impeller in the radial direction of the impeller. The entire axial inclined portion is provided with an axial air outlet 8 of the impeller, and the impeller blade disc 7 is provided at the middle portion of the axial side of the impeller. . The impeller front side of the impeller has no impeller blade disc and is provided with a semi-straddle impeller blade synchronous baffle booster 6 and a synchronous downstream air inlet port 9, and the rear outer side of the impeller is provided with a casing connected to the side wall of the casing. The axial outlet baffle 10 is provided with a conical tubular wind-shielding guide ring 11 connected to the side wall of the casing at the axially outer side of the impeller, and a reinforcing lacing 12 is respectively arranged on the axial rear side of the impeller axially. The impeller is rotated by the motor 16.

During operation, the entire front axial side of the impeller (the front end of the air inlet of the casing is the front end, the air outlet end is the rear end, the air inlet side of the impeller is the axial front side, and the exhaust side is the axial rear side). The air inlet 9 sucks the gaseous substance from the air inlet 2 of the casing on the axial front side of the cylindrical casing, and then discharges the processed airflow axially from the axial air outlet 8 of the impeller axial side. The airflow is then diverted into a standard axial airflow through the axially outer casing axial outlet baffle 10 after the impeller, and then discharged to the casing air outlet 3. During the working process, the axial direction of the impeller axial side of the impeller is axially inclined. The exhaust airflow collides with the fine swirling airflow generated by the side wall of the casing, and is blocked by the wind deflector 11 provided on the axial outer side of the impeller. The synchronous downstream air inlet 9 leading to the axial side of the impeller is again sucked into the impeller. The windshield diversion ring ensures that the fan has a good suction and discharge effect.

In this embodiment, since the airflow is centrifugally synchronized, the entire front axial side of the flow fan is pumped and the centrifugal blade is used for processing, so that the air volume is large and the wind pressure is high; and In the form of a radial tilt, the airflow enters the impeller axially from the air inlet of the casing and is not abruptly turned. For radial flow, it is inclined or flowing in the axial direction, so that it can avoid the formation of intense eddy current and reduce the eddy current loss. Therefore, the efficiency of this example is high, and since the impeller air outlet is axial. The airflow from the axial air outlet of the impeller does not collide with the side wall of the casing, so the fan noise is very low.

This example is suitable for various axial flow fans to replace various old axial fans, diagonal flow fans, and mixed flow fans.

Embodiment 2 (refer to FIG. 4 and FIG. 5), the multi-functional synchronous rear-flow ventilation compressor, this example is basically the same as the example 1, except that the casing of the present example is a variant volute type centrifugal fan casing. The casing air outlet 3 is disposed on the radial side wall of the casing, and the outlet direction is a radial axial type. The impeller adopts the single-blade (only thrust wall) structure of the old centrifugal fan. The axial front side and the axial rear side of the impeller are gradually inclined from the front to the rear of the impeller in the radial direction of the impeller, and the impeller blades 5 are radially along the impeller. Then the width is the same. Impeller blade disc 7 is arranged on the axial rear side of the impeller axial front side, and the middle part of the impeller axial front side is provided with a special air inlet 13 3 in the middle of the impeller, and the entire impeller is closed. The radial end of the impeller is provided with an impeller radial air outlet 14, the outlet direction is radial axial, and the rear axial side of the impeller does not have an impeller axial air outlet, and the inner airflow passage of the impeller is axially radial downstream.

During operation, the airflow enters the special air inlet 13 in the middle of the impeller from the air inlet 2 of the axial casing of the casing, and then enters the impeller in the radial direction of the impeller. The radial air outlet 14 is then discharged to the casing diffuser passage.

During the whole working process, the airflow enters the air inlet from the casing axially into the middle of the impeller. The special air inlet 13 is basically along the axial direction (axial radial oblique direction) and enters the inner airflow passage 15 of the impeller, downstream, avoiding the axial direction. The sharp turn to the radial direction produces intense eddy currents, avoiding eddy current losses, and thus the fan is high in efficiency and low in noise. Moreover, because the airflow enters the impeller through the special air inlet at the middle of the impeller, and then flows out from the impeller at the radial end of the impeller, the radial flow of the airflow is large, and the energy is absorbed, so the turbocharged effect is good.

This example is adapted to be used as a high pressure fan. The impeller of this example is also suitable for several high-pressure ultra-high pressure blowers, compressors and gas compressors.

Embodiment 3 (Refer to Fig. 6, Fig. 2, Fig. 3), the multi-functional synchronous rear-flow ventilation compressor, this example is basically the same as the example 1, except that the rotor of this example is connected in series with the same drive shaft. The flow fan impeller is combined. The axial front side of each impeller is axially inclined from the front to the rear of the impeller in the radial direction of the impeller, and the axial inclination angle is equal, and the impeller blades are radially along the impeller. The width is the same before and after. The impeller blade disc is not provided on the axial front side of the first stage impeller, and the entire front axial side is provided with a synchronous downstream air inlet port 9, and the entire front axial side surface sucks the object substance externally. The impeller axial air outlet 8 is provided on the axial rear side of the impeller, and the impeller blade disc is disposed on the axial front side of the three impellers after the first stage, and the axial side of the impeller is radially rearward. The rear part (close to the radial end of the impeller) is provided with an axial impeller 8 at the end impeller. The middle part of the axial side of the impeller is provided with a special air inlet 13 at the middle of the impeller. A conical tubular wind deflector 11 connected to the side wall of the casing, each of the wind deflector outlets 17 is directed to an intermediate impeller 13 for the impeller intermediate axial side of the adjacent impeller. A casing axial outlet baffle 10 is disposed axially rearward of the rotor at the final stage of the rotor. The entire rotor is coupled to the drive shaft 28 via a coupling 18 and is driven to rotate by a diesel engine.

During operation, the entire axial front side of the first stage impeller draws gaseous material through its synchronous downstream air inlet 9, so the flow rate is large. The large flow gas sucked by the first stage impeller is processed and discharged into the rear axial expansion chamber of the rotor, and then decelerated and pressurized, and then discharged to the wind deflector 11 and guided by the wind deflector to the middle of the secondary impeller. The special air inlet 13 enters the second-stage impeller, and the second-stage impeller increases the speed of the airflow processing, and then discharges in the axial expansion region of the rear rotor 19 to decelerate and pressurize, and then discharges the wind-shielding guide ring 11 behind it. The wind diversion ring is redirected into the third-stage impeller in the middle of the three-stage impeller. The third-stage impeller is then increased in speed and then discharged to the wind-guiding guide ring 11, and then guided into the fourth-stage impeller. The tuyere enters the four-stage impeller, and the fourth-stage impeller increases the speed of the airflow processing, and then passes through the axial rear side radial rear rear axial air outlet port in the axial rear side casing axial outlet deflector 1 After finishing the Q into a standard axial airflow, the Q is discharged.

During the whole working process, the airflow flows from the first stage impeller and then flows in the axial direction. Although the middle is guided by the wind deflector 11 , the wind deflector 11 has a simple structure, short flow path and less bending. The eddy current is small, the friction loss is small, the efficiency is high, and the noise is low. Since the third-stage impeller after the first stage is sucked by the intermediate special air inlet, it is discharged from the radial end, the radial flow of the air flow is large, the energy is absorbed, and the supercharging effect is obtained. it is good.

This example is suitable for use in various high-pressure ultra-high pressure compressors and gas compressors.

In this case, it is also possible to use concentric two-axis, concentric three-axis or concentric four-axis series several or more than one impeller of this structure, and several rotors of different speeds and different pressures are assembled with high-pressure ultra-high pressure blower or high-pressure ultra-high pressure compressor gas. Used by the compressor.

Embodiment 4 (refer to FIG. 7), the multi-functional synchronous rear-flow ventilation compressor, this example is basically the same as the example 3, except that the casing of the present example is a cylindrical combined spiral cylinder, and the first three-stage impeller is placed in the cylindrical cylinder. Machine Inside the casing, the final impeller is placed in a spiral casing, and the casing air outlet 3 is disposed on the radial side wall of the spiral casing, and the outlet direction is radial. The second difference is that in the latter three stages of the impeller, the front side of the impeller does not have a special air inlet at the middle of the impeller, and the impeller blade disc is not provided at the rear of the radial direction, and the impeller vane 7 is arranged at the radial front. The third difference is that in this case, the impellers are not connected to the windshield guide ring of the side wall of the casing. The fourth difference is that the axial rearward part of the impeller is axially rearward. The impeller axial air outlet 8 is provided.

During operation, the entire axial front side of the first stage impeller draws gaseous material through its synchronous downstream air inlet 9, so the compressor flow is large. The large flow gas sucked by the first stage impeller is processed and discharged into the axial expansion chamber 19 of the rear rotor, and then discharged to the secondary impeller. The second impeller is axially sucked through the synchronous downstream air inlet 9 After being processed and discharged in the axial expansion of the rotor, the deceleration is supercharged and then discharged to the third impeller. The third impeller is further processed, and then discharged in the axial expansion of the rotor to be decelerated and expanded, and then discharged to the fourth. The impeller, the fourth impeller is again sucked and then processed, and then discharged into the axial expansion of the spiral casing to reduce the pressure, and finally discharged from the air outlet 3 of the casing, and the airflow passes through four synchronous blower impellers. After that, high energy can be obtained, so the wind pressure is high.

There is no static guiding device between the two impellers of the whole structural system rotor. During the whole working process, after the airflow is sucked from the first impeller, the flow in the rotor flow channel absorbs the energy to increase the pressure, the working flow path is short, and the bending is tortuous. Less, so the friction loss is small, and the noise will naturally be low.

Obviously, compared with the traditional old axial flow or centrifugal compressor, this example is simple in structure, less in material consumption, light in weight, saves resources, convenient in handling and installation, good in boosting effect, high in efficiency, energy saving, low noise. , is conducive to environmental protection. Due to its low material consumption, small size and light weight, this example is especially suitable for use on vehicles, ships and aircraft engines.

Embodiment 5 (refer to FIG. 8 and FIG. 9), the multi-functional synchronous rear-flow ventilation compressor, this example is basically the same as the example 4, except that the casing of the present example is provided with an axial front side wall and a casing air inlet. 2 is disposed on the axial front side wall, and the air inlet 2 of the casing is a horn type which is expanded from the front to the rear, and a cone-shaped diffusion flow divider 20 which is expanded from the front and the rear is provided inside and outside the inlet of the air inlet of the casing, and the diffuser 20 is diffused. A connecting baffle 21 is provided, and the diffusing splitter 20 is connected to the side wall of the air inlet of the casing through the connecting baffle 21. The second difference is that the second, third and fourth stage impellers are multi-walled blade structural type (including thrust wall 22, negative pressure separation wall 23, negative pressure gap 24), and impeller blade discs are not provided on the axial side of the impeller. No intermediate dedicated The tuyere, the impeller axial rear side is radially rear and the rear part is provided with an end impeller axial air outlet 8. The third difference is that, in this example, the wind deflector 11 connected to the casing is disposed axially behind each impeller in the first three stages of the entire rotor, and the wind deflector outlet 17 is directed to the adjacent rear impeller. Radial front of the front axial side. In this example, the four impellers are provided with reinforcing ribs 12 on the axial rear side of the front side of the impeller.

During operation, the airflow drawn by the "eight-shaped air inlet" is diffused downstream by the diffusion splitter to the synchronous downstream air inlet 9 of the first-stage synchronous after-flow fan impeller, and then flows into the inner airflow passage of the impeller to process the absorbed energy. Then, the impeller is discharged from the impeller axial air outlet 8 on the rear side of the impeller, and is decelerated and pressurized by the axial expansion of the rotor 19, and then enters the wind deflector 11 to be diverted by the wind deflector 11 The second-stage multi-wall blade structure impeller is radially front and is machined by the stage impeller. Then the impeller axial rear side radial rear rear end end of the impeller axial air outlet 8 is arranged in the rear rotor axial expansion and deceleration The pressure is then guided into the third-stage impeller by the wind-shielding guide ring, and then decelerated and expanded by the axial expansion of the rotor 19, and then guided to the fourth stage by the wind-shielding guide ring 11 thereafter. The impeller is decelerated and supercharged by machining, and finally discharged into the axial expansion flow passage of the screw casing, and then discharged from the air outlet 3 of the casing.

During the whole work process, due to the function of the diffusing diverter, the airflow enters the air inlet of the casing, and basically flows downstream, with less bending and tortuosity, less eddy current loss, good supercharging effect, high efficiency and low noise.

This example is adapted to be used as a high pressure blower, a high pressure extra high pressure compressor, and a gas compressor.

Embodiment 6 (refer to FIG. 9 and FIG. 10), the multi-functional synchronous rear-flow ventilation compressor, this example is basically the same as the example 5, except that the casing of the present example is a cylindrical cone-shaped cylinder combination type, and the body axial front The part is a cylindrical casing, and the axial rear part is a conical cylinder casing which is expanded from the rear to the front. (The structure is provided with the motor side being the axial rear side and the opposite side being the axial direction. The front side, the first impeller part refers to the same type of pushing), the conical cylinder casing is provided with two coaxially connected impellers, and the axial rear side wall of the conical cylinder is provided with the casing axial rear side air inlet 25. The axial front side wall of the cylindrical casing is provided with the casing air inlet 2, the radial side wall is provided with the casing air outlet 3, and the outlet direction of the casing air outlet 3 is radial. The second difference is that the rotor of this example consists of two impellers. Both impellers are located on the axial front side of the cone casing. The first impeller is a three-wall impeller structure type rear-flow fan impeller. The front and rear side walls are provided with a small impeller vane 7 only in the middle part, and a negative pressure gap 24 is arranged on the front and rear sides of the impeller, and both can be sucked out. The body material, the radial end of the impeller is provided with an impeller radial air outlet 14. The second impeller of the rotor is a synchronous rear fan impeller, and its axial front and rear sides are axially rearward and backward toward the impeller axial rearward along the impeller (the impeller inlet side is the axial front side forward, and the corresponding one The side is axial rear side rearward) gradually inclined axially. The impeller axial front side is provided with a synchronous flow guiding supercharger 6, and a synchronous downstream air inlet port 9, and the axial rear side axial inclined portion is provided with an impeller axial direction. The air outlet 8 is provided with an impeller radial air outlet 14 at the radial end of the impeller. The third difference is that the outer side of the outlet end of the air inlet 2 of the casing is provided with a diffusing splitter 20 which is expanded from the front to the rear. The diffusing splitter 20 is provided with a connecting baffle 21, and the diffusing splitter 20 is connected through the connecting flow. The piece 21 is connected to the inner side wall of the air inlet of the casing, and the first impeller axially front side of the rotor is provided with a cone-shaped drainage diffuser 26 connected to the impeller blade disk from the front and the rear to expand, and the rotor is rotated by the motor 16.

During operation, after the second synchronization of the rotor, the blower impeller is sucked into the clean air from the axial rear air inlet 25 of the casing to be processed into a high-speed airflow, and then directly discharged to the rotor by the axial air outlet 8 of the impeller and the radial air outlet 14 of the impeller. The first rear-flow fan impeller, the rear-flow fan impeller reprocesses the high-speed airflow into a higher-speed airflow, and a higher-speed clean air flow flows through and out of the rear-flow fan impeller, which will form on the axial front side of the impeller. The strong cyclone high negative pressure zone, the strong cyclone high negative pressure zone will be able to suck the external polluting gas into the inner side of the casing through the air inlet 2 of the casing, and the polluting gas entering the inner side of the casing has a diffusion splitter 20 and a drainage diffuser 26 The isolation and diversion function, the pollutant gas can not be contacted and cannot enter the impeller, but is directly discharged from the casing through the casing air outlet 3 by the action of a cyclone.

During the whole work process, a large amount of polluting gas substances (or contaminated liquids and solid materials) sucked by the strong cyclone high negative pressure do not contact the impeller and do not pollute the impeller. Compared with the above several examples, the sample example still consumes less energy and has low noise.

This example is suitable for use as a variety of air and dust removal blowdown fans to absorb pollutants (including gases, liquids, solid materials), acid and alkali salts, high temperature materials.

Embodiment 7 (refer to FIG. 1 1 ), the multi-functional synchronous rear-flow ventilation compressor, this example is basically the same as the example 6 except that the axial front part of the casing is a conical cylinder shape, and the conical cylinder is composed of Front and rear expansion, the axial front side wall is provided with the casing air inlet 2, the rear part of the casing is cylindrical, the radial side wall of the cylinder is provided with the casing air outlet 3, and the rear axial side wall is provided with a machine The shell axial rear side air inlet 25 (the motor side is the rear side of the body or the impeller shaft, the rear side, and the opposite side is the axial front side, the front side). The second difference of this example is that the rotor has only one three-walled blade structure impeller. The front and rear sides of the impeller are gradually inclined axially from the front to the rear of the impeller in the radial direction of the impeller, and the axial direction of the front and rear sides of the impeller is small. The impeller blade disc 7 has a negative pressure separating wall and a negative pressure gap on both sides of the impeller, that is, both sides can suck foreign matter, and the radial end of the impeller is provided with an impeller radial air outlet 14, the impeller The axially front side intermediate outer side is provided with a spherical crown-shaped drainage diffuser 26 which is expanded from the front and the rear, and the drainage diffuser is provided with a drain connector 27 at the axial rear end, and the drainage diffuser 26 is connected to the impeller intermediate impeller by the drain connector Leaf disc connection. The drainage diffuser 26 can block the axially outer side of the impeller from contacting the impeller.

During operation, the axial back pressure of the impeller is sucked into the impeller through the air inlet 25 of the axial rear side of the casing to be processed into a high-speed airflow. The high-speed airflow forms a strong cyclone high negative pressure zone on the front side of the impeller. The high cyclone zone of the cyclone causes foreign matter (including solid, liquid, and gaseous substances) to enter the inside of the casing through the air inlet 2 of the casing, but enters the casing through the air inlet of the casing due to the blocking of the axially outward drainage diffuser of the impeller. The external material on the axial front side of the inner impeller does not contact the impeller, and does not contaminate the impeller. The clean air sucked in by the axial rear air inlet 25 of the casing can both cool the impeller and create a strong cyclone high negative pressure zone for the front side of the impeller shaft.

This example is similar to the example 6 and is suitable for use in various types of air blower and dust blower. More importantly, this example is especially suitable for use in various dust collectors, sweepers, and road sweepers. Any substance (such as cloth sheet, clothing bag, branch leaves, etc.) However, the impeller does not block the impeller and does not deface the impeller.

Embodiment 8 (refer to FIG. 12), the multi-functional synchronous rear-flow ventilation compressor, this example is basically the same as the first example, except that the axial front side of the impeller is gradually curved from the front to the rear of the impeller in the radial direction of the impeller. To the inclination, the axial rear side of the impeller is gradually inclined axially from the front to the rear of the impeller in the radial direction of the impeller. The axial rear side of the impeller is axially inclined from the front to the rear in the radial direction of the impeller. The impeller is radially expanded and widened from front to back toward the axial forward and axial rear of the impeller; the inner flow passage 15 of the impeller gradually expands and widens in the radial direction of the impeller from the front to the rear toward the axial rear of the impeller and the axial front.

During operation, the airflow enters the special air inlet 13 of the impeller axially from the air inlet 2 of the axial side wall of the casing, and then enters the inner airflow passage 15 of the impeller radially toward the front side of the impeller and the axial rear side. The axial expansion flow, gradually decelerating the pressure, and then flowing out of the impeller from the radial outlet 14 of the impeller at the radial end of the impeller, and then flowing into the expansion chamber of the casing.

During the whole working process, the airflow enters the special air inlet 13 in the middle of the impeller from the air inlet of the casing, and the deceleration and supercharging flow in the axially expanding airflow passage after entering the airflow passage 15 inside the impeller. After flowing into the diffuser passage of the casing, it is decelerated and pressurized. When the air flows out of the air outlet of the casing, the wind pressure will be high, and the wind speed at the impeller exit will be very low, so the noise will be low.

This example is suitable for use in a variety of high pressure fan blowers.

Embodiment 9 (refer to FIG. 13), the multi-functional synchronous rear-flow ventilating compressor, this example and the example 2 are basically the same, except that the casing of the present example is a cylindrical cone-shaped combined casing, a cone-shaped portion The shaft is expanded from the rear to the front in the axial direction of the body, the impeller is placed in the cone, the air inlet 2 of the casing is disposed on the axial front side of the cylindrical portion, and the air outlet 3 of the casing is disposed on the radial side wall of the cylindrical cylinder. The second difference is that the impeller of this example is a multi-walled blade structure. The front side of the impeller is not provided with a blade disc. The axial front side and the axial rear side of the impeller are axially forward from the front to the rear of the impeller. The axial inclination is gradually inclined, and their axial inclination angles are equal. The impeller blades 5 are the same width from the front to the rear in the impeller radial direction, and the inner flow passage 15 of the impeller is equi-sectioned from the front to the rear in the radial direction of the impeller. The radial direction of the impeller at the radial end of the impeller 14 is the direction of the radial direction of the axial direction of the impeller.

During operation, the impeller axial front side negative pressure gap draws part of the gas into the impeller through the casing air inlet 2, and the impeller processes the gas into a high-speed airflow, and the high-speed airflow is made up of the impeller radial end of the impeller. The radial inclination is discharged (rotating flow along the side wall of the casing of the cone), and the high-speed airflow discharged from the impeller rotates at a high speed on the front side of the impeller axial direction, thereby causing a strong cyclone high negative pressure zone on the front side of the impeller. The strong cyclone high negative pressure zone will be able to suck a large amount of gaseous substances into the inner side of the casing through the air inlet 2 of the casing, and then be discharged from the body through the air outlet 3 of the casing. During the whole working process, a large amount of external gas substances sucked by the negative pressure of the strong whirlwind high negative pressure zone on the front side of the impeller does not contact the impeller and does not enter the impeller, and does not pollute the impeller. This example is suitable for use in various dust removal and blowdown fans to absorb pollutants or waste materials or to produce useful materials in daily life.

Embodiment 10 (refer to FIG. 14), a multi-functional synchronous rear-flow ventilating compressor, this example is basically the same as in Example 1, except that the impeller axial front side and the axial rear side of this example are radially forward and backward along the impeller. The axial inclination of the axial direction of the impeller is gradually inclined, and the axial inclination angle of the front side of the impeller is smaller than the axial inclination angle of the axial direction of the impeller, and the impeller blade 5 gradually contracts axially from the front to the rear in the radial direction of the impeller.

In operation, the performance characteristics of this example are the same as in Example 1. This example is also suitable for use in various axial flow fans.

Embodiment 11 (Refer to Fig. 9, Fig. 10, Fig. 11, Fig. 15), the multi-functional synchronous rear-flow ventilating compressor, this example is basically the same as the example 1, except that the impeller axial rear side of the present example is along the impeller diameter. Gradually axially inclined from the front to the rear toward the axial direction of the impeller, the front side of the impeller is axially forward and backward along the impeller The axial inclination angles are gradually equal to the axial rear of the impeller, and the entire impeller blades 5 are gradually inclined and narrowed from the front to the rear in the radial direction of the impeller.

The performance characteristics of this example are the same as in Example 1. This example is also suitable for use in various axial flow fans. Industrial applicability

The multifunctional synchronous backflow ventilation compressor of the invention is suitable for the field of air purification compression technology, and the entire front axial side of the impeller of this structure (the impeller blade disc or the small impeller blade disc) can be almost externally The gas substance is pumped, and the centrifugal type is added. Therefore, the impeller has a large flow rate and a good pressurization effect, and can be widely applied to various ventilators, compressors, gas compressors, and the like.

Claims

Rights request

1. Multi-functional synchronous rear-flow ventilation compressor, including organic shell (1), casing air inlet (2), casing air outlet (3), impeller (4), impeller blades (5), impeller inner air passage (15) an impeller blade disc (7), characterized in that the axial front side of the impeller blade (5) is gradually axially inclined from the front to the rear of the impeller toward the axial direction of the impeller, and the axial side of the impeller blade (5) The impeller is gradually inclined axially from front to back toward the axial direction of the impeller. The axial front side of the impeller (4) is gradually inclined axially from the front to the rear of the impeller toward the axial direction of the impeller. The axial direction of the impeller (4) is along the impeller diameter. The axial direction of the impeller is gradually inclined axially from the front to the rear of the impeller. The inner flow passage (15) of the impeller is gradually inclined axially from front to back toward the axial direction of the impeller in the radial direction of the impeller. The axial rear side of the impeller is directed from the front and the rear toward the impeller shaft in the radial direction of the impeller. An impeller blade disc (7) having a tapered cylindrical structure is provided to one of the gradually axially inclined portions.

2. The multi-functional synchronous backflow ventilator according to claim 1, wherein the axial rear side of the impeller is provided with an axial air outlet of the impeller along the radial direction of the impeller from the front to the rear toward the axial direction of the impeller. 8 ).

A multi-function synchronous backflow ventilating compressor according to claim 1, wherein the impeller shaft is inclined toward the rear side in the radial direction of the impeller from the front to the rear toward the axial direction of the impeller.

A multi-function synchronous backflow ventilating compressor according to claim 1, 2 or 3, characterized in that the radial end of the impeller is provided with an axially radially inclined impeller radial air outlet (14).

5. The multi-functional synchronous backflow ventilating compressor according to claim 1, 2 or 3, wherein a wind deflecting flow in the form of a cone-shaped cylinder structure is provided between the two impellers in the airflow passage inside the casing. ring

(11) The expansion end of the wind deflector (11) is connected to the inner side wall of the casing.

The multi-function synchronous backflow ventilating compressor according to claim 1, 2 or 3, wherein the casing (1) is in the form of a variant volute structure.

6. The multi-functional synchronous backflow ventilating compressor according to claim 1, 2 or 3, characterized in that the axial side of the impeller is provided with a drainage diffuser (26) in the form of an expansion structure from the front to the rear, and a drainage diffuser ( 26) Connected to the impeller (4).

7. The multi-functional synchronous backflow ventilating compressor according to claim 1, 2 or 3, wherein the air inlet (2) of the casing is provided with a diffusion splitter (20) in the form of an expanded structure from front to back. The diffusion diverter (20) is provided with a connecting baffle (21), and the diffusion diverter (20) is connected to the side wall of the air inlet (2) of the casing through the connecting baffle (21).