阅读说明：本技术 一种叶轮总成及输送泵 (Impeller assembly and delivery pump ) 是由 刘洪福 冯宪 肖虎 李孝凡 于 2021-09-15 设计创作，主要内容包括：本申请实施例提供一种叶轮总成及输送泵,属于泵送设备技术领域,该叶轮总成具有转动中心线以及位于转动中心线周围的流道,叶轮总成包括两个叶轮主体,每个叶轮主体绕转动中心线转动,两个叶轮主体沿转动中心线的延伸方向相对布置,两个叶轮主体围设成流道,两个叶轮主体通过相互靠近或远离改变流道的过流面积以调节流道的流量。通过两个叶轮主体的相互靠近和远离,使流道的过流面积发生变化,从而调节输送泵的流量,在输送泵的流量调节过程中,不需要改变叶轮主体的转速,因而不需要在电网中增加变频器,降低了输送泵在流量调节过程中给电网造成的污染。(The embodiment of the application provides an impeller assembly and delivery pump, belong to pumping equipment technical field, this impeller assembly has the rotation center line and is located the runner around the rotation center line, impeller assembly includes two impeller main parts, every impeller main part revolves the rotation center line and rotates, two impeller main parts are arranged along the extending direction looks mutual of rotation center line, two impeller main parts enclose and establish the runner, two impeller main parts are through being close to each other or keeping away from the flow area that changes the runner with the flow of adjusting the runner. The flow area of the flow channel is changed by the mutual approaching and separating of the two impeller main bodies, so that the flow of the delivery pump is adjusted, and the rotating speed of the impeller main bodies does not need to be changed in the flow adjusting process of the delivery pump, so that a frequency converter does not need to be added in a power grid, and the pollution of the delivery pump to the power grid in the flow adjusting process is reduced.)

1. The impeller assembly is characterized by comprising a rotation center line and flow channels located around the rotation center line, the impeller assembly comprises two impeller main bodies, each impeller main body rotates around the rotation center line, the two impeller main bodies are oppositely arranged along the extension direction of the rotation center line, the two impeller main bodies are arranged in the flow channels in a surrounding mode, and the two impeller main bodies are close to or far away from each other to change the flow passing area of the flow channels so as to adjust the flow of the flow channels.

2. The impeller assembly of claim 1 wherein the impeller body includes vanes, the vanes of both of the impeller bodies being partially stacked to limit leakage of fluid within the flow passage from between the vanes of both of the impeller bodies.

3. The impeller assembly of claim 2 wherein the vanes of the two impeller bodies are sealingly connected to limit leakage of fluid within the flow passage from between the vanes of the two impeller bodies.

4. The impeller assembly of claim 1 further comprising a shaft assembly, wherein the impeller body is sleeved on the shaft assembly, and wherein the impeller body is capable of moving in an axial direction of the shaft assembly.

5. The impeller assembly of claim 4, wherein the shaft assembly comprises:

installing a shaft; and

the axle sleeve, the cover is located the installation axle, the axle sleeve can be followed the axial displacement of installation axle, at least one impeller main part cover is located the axle sleeve, the axle sleeve is used for driving the impeller main part for installation axle is along axial displacement.

6. The impeller assembly of claim 5, wherein the bushing comprises:

the first sub-shaft sleeve is sleeved on the installation shaft, can move along the axial direction of the installation shaft and rotates along with the installation shaft, the corresponding impeller main body is sleeved on the first sub-shaft sleeve so as to enable the corresponding impeller main body to rotate along with the first sub-shaft sleeve, and a first shaft shoulder is formed at one end of the first sub-shaft sleeve; and

the second sub-shaft sleeve is sleeved on the installation shaft and can move along the axial direction of the installation shaft, the second sub-shaft sleeve is installed at one end, deviating from the first shaft shoulder, of the first sub-shaft sleeve, a second shaft shoulder is formed on the second sub-shaft sleeve, and an area between the first shaft shoulder and the second shaft shoulder is used for at least partially accommodating the corresponding impeller main body so as to limit the corresponding impeller main body to move along the axial direction of the installation shaft.

7. The impeller assembly of claim 6, wherein each of the first sub-bushings is formed with internal splines on an inner side thereof, the mounting shaft is formed with external splines engaging the internal splines, and the outer side of the first sub-bushings is fixedly connected to the impeller body.

8. The impeller assembly of claim 5, wherein the number of the shaft sleeves is two, the two shaft sleeves are arranged oppositely along the axial direction of the mounting shaft, the impeller assembly further comprises a sealing sleeve, the sealing sleeve is arranged at one end of the two impeller bodies close to each other, the shaft sleeves and the corresponding impeller bodies are sealed by the sealing sleeve to prevent the fluid in the flow passage from leaking from between the two impeller bodies, and the sealing sleeve is spanned between the two shaft sleeves to prevent the fluid in the flow passage from leaking from between the two shaft sleeves.

9. The impeller assembly of claim 8, wherein the end of the two impeller bodies close to each other is enclosed into a sealing groove, the sealing sleeve is installed in the sealing groove, the sealing groove has two annular grooves oppositely arranged along the axial direction of the installation shaft, the sealing sleeve is formed with two installation convex rings oppositely arranged along the axial direction of the installation shaft, each installation convex ring is located in the corresponding annular groove, and each installation convex ring is in sealing abutment with the corresponding shaft sleeve and the impeller body respectively so as to restrain the installation convex ring in the annular groove.

10. The impeller assembly of claim 7, wherein the number of the bushings is two, the two bushings being arranged opposite each other in an axial direction of the mounting shaft, the mounting shaft including:

the two first shaft sections are respectively corresponding to the first sub-shaft sleeves and the second sub-shaft sleeves, and the first sub-shaft sleeves and the second sub-shaft sleeves can move along the axial direction of the corresponding first shaft sections; and

the second shaft section is connected between the first shaft sections, the first sub shaft sleeves are all sleeved on the second shaft section, the diameter of the second shaft section is larger than that of the first shaft section, and two ends of the second shaft section can be respectively abutted to the end portions of the corresponding internal splines to enable the corresponding first sub shaft sleeves to be positioned.

11. The impeller assembly of claim 10, wherein the second shaft section is sealingly connected to both of the first subshaft sleeves to prevent fluid within the flow passage from leaking between the second shaft section and the first subshaft sleeves.

12. The impeller assembly of claim 5 wherein said mounting shaft is keyed to said bushing.

13. The impeller assembly of claim 5 further comprising a connection mechanism connected to said bushing, said connection mechanism being rotatable about said bushing.

14. A delivery pump, comprising:

an impeller assembly according to any one of claims 1 to 13; and

the impeller assembly is arranged on the pump shell and rotates around a rotation center line so as to convey fluid in the pump shell.

15. The delivery pump of claim 14, further comprising two traction mechanisms, each of said traction mechanisms being connected to a corresponding said impeller body, each of said traction mechanisms driving a corresponding said impeller body to move said two impeller bodies toward or away from each other.

Technical Field

The application relates to the technical field of pumping equipment, in particular to an impeller assembly and a delivery pump.

Background

In the use process of the delivery pump, the flow of the delivery pump may need to be adjusted, and in the related art, the output power of a motor for driving an impeller to rotate often needs to be adjusted based on a frequency converter, so that the cost of flow adjustment of the delivery pump is high, and the flow adjustment mode of the delivery pump may cause grid pollution.

Disclosure of Invention

In view of the above, it is desirable to provide an impeller assembly and a delivery pump to reduce the cost of flow regulation and the pollution to the power grid during the flow regulation process.

In order to achieve the above object, an aspect of the embodiments of the present application provides an impeller assembly, which has a rotation center line and is located a flow channel around the rotation center line, the impeller assembly includes two impeller main bodies, each impeller main body winds the rotation center line rotates, two the impeller main body is along the extending direction of the rotation center line is arranged relatively, two the impeller main body encloses into the flow channel, two the impeller main body changes through being close to each other or keeping away from the flow area of the flow channel in order to adjust the flow rate of the flow channel.

In one embodiment, the impeller body includes vanes, and the vanes of two impeller bodies are partially overlapped to restrict fluid in the flow passage from leaking between the vanes of the two impeller bodies.

In one embodiment, the vanes of the two impeller bodies are sealingly connected to restrict fluid in the flow passage from leaking between the vanes of the two impeller bodies.

In one embodiment, the impeller assembly further includes a shaft assembly, the impeller main body is sleeved on the shaft assembly, and the impeller main body can move along the axial direction of the shaft assembly.

In one embodiment, the shaft assembly comprises:

installing a shaft; and

the axle sleeve, the cover is located the installation axle, the axle sleeve can be followed the axial displacement of installation axle, at least one impeller main part cover is located the axle sleeve, the axle sleeve is used for driving the impeller main part for installation axle is along axial displacement.

In one embodiment, the bushing includes:

the first sub-shaft sleeve is sleeved on the installation shaft, can move along the axial direction of the installation shaft and rotates along with the installation shaft, the corresponding impeller main body is sleeved on the first sub-shaft sleeve so as to enable the corresponding impeller main body to rotate along with the first sub-shaft sleeve, and a first shaft shoulder is formed at one end of the first sub-shaft sleeve; and

the second sub-shaft sleeve is sleeved on the installation shaft and can move along the axial direction of the installation shaft, the second sub-shaft sleeve is installed at one end, deviating from the first shaft shoulder, of the first sub-shaft sleeve, a second shaft shoulder is formed on the second sub-shaft sleeve, and an area between the first shaft shoulder and the second shaft shoulder is used for at least partially accommodating the corresponding impeller main body so as to limit the corresponding impeller main body to move along the axial direction of the installation shaft.

In one embodiment, an inner spline is formed on an inner side of each first sub-sleeve, an outer spline engaged with the inner spline is formed on the mounting shaft, and an outer side of each first sub-sleeve is fixedly connected with the impeller main body.

In one embodiment, the number of the shaft sleeves is two, the two shaft sleeves are arranged oppositely along the axial direction of the mounting shaft, the impeller assembly further includes a sealing sleeve, the sealing sleeve is located at one end where the two impeller bodies are close to each other, the shaft sleeves and the corresponding impeller bodies are sealed by the sealing sleeve to prevent the fluid in the flow passage from leaking between the two impeller bodies, and the sealing sleeve is spanned between the two shaft sleeves to prevent the fluid in the flow passage from leaking between the two shaft sleeves.

In one embodiment, two one end that impeller main part is close to each other encloses into the seal groove, the seal cover is installed in the seal groove, the seal groove has along two ring channels of the axial relative arrangement of installation axle, the seal cover is formed with along two installation bulge loops of the axial relative arrangement of installation axle, every installation bulge loop is located correspondingly in the ring channel, every installation bulge loop respectively with correspond the sealed butt of axle sleeve and impeller main part is in order to be in with the installation bulge loop restraint is in the ring channel.

In one embodiment, the number of the shaft sleeves is two, and the two shaft sleeves are oppositely arranged along the axial direction of the mounting shaft, and the mounting shaft includes:

the two first shaft sections are respectively corresponding to the first sub-shaft sleeves and the second sub-shaft sleeves, and the first sub-shaft sleeves and the second sub-shaft sleeves can move along the axial direction of the corresponding first shaft sections; and

the second shaft section is connected between the first shaft sections, the first sub shaft sleeves are all sleeved on the second shaft section, the diameter of the second shaft section is larger than that of the first shaft section, and two ends of the second shaft section can be respectively abutted to the end portions of the corresponding internal splines to enable the corresponding first sub shaft sleeves to be positioned.

In one embodiment, the second shaft section is connected with both of the first sub-bushings in a sealing manner to prevent fluid in the flow passage from leaking between the second shaft section and the first sub-bushings.

In one embodiment, the mounting shaft is keyed to the bushing.

In one embodiment, the impeller assembly further comprises a connecting mechanism connected with the shaft sleeve, and the connecting mechanism can rotate around the shaft sleeve.

A second aspect of the embodiments of the present application provides a delivery pump, including:

an impeller assembly according to any of the above; and

the impeller assembly is arranged on the pump shell and rotates around a rotation center line so as to convey fluid in the pump shell.

In one embodiment, the delivery pump further includes two traction mechanisms, each of the traction mechanisms is connected with a corresponding impeller body, and each of the traction mechanisms drives the corresponding impeller body to move so as to enable the two impeller bodies to approach or move away from each other.

According to the impeller assembly provided by the embodiment of the application, when the two impeller main bodies are close to each other, the width of the flow channel is reduced, the flow area of the flow channel is correspondingly reduced, and the flow of the delivery pump can be reduced to a certain extent under the condition that the rotating speed of the impeller main bodies is basically unchanged; when the two impeller main bodies are far away from each other, the width of the flow channel is increased, the flow area of the flow channel is correspondingly increased, and the flow rate of the delivery pump can be increased to a certain extent under the condition that the rotating speed of the impeller main bodies is basically unchanged. The flow area of the flow channel is changed by approaching and separating the two impeller main bodies, so that the flow of the delivery pump is adjusted, and the rotating speed of the motor is not required to be changed in the flow adjusting process of the delivery pump, so that a frequency converter is not required to be added in a power grid, the flow adjusting cost of the delivery pump is reduced, and the pollution of the delivery pump to the power grid in the flow adjusting process is reduced. It can be understood that, the rotating speed of the impeller main body is unchanged, the flow rate of the flow channel is changed, the output power of the motor for driving the impeller main body to rotate is correspondingly changed, and a frequency converter is not needed for changing the output power of the motor.

Drawings

FIG. 1 is a schematic structural diagram of an impeller assembly according to an embodiment of the present application;

fig. 2 is an assembly view of two impeller bodies according to an embodiment of the present application, showing a position state of the two impeller bodies when a flow passage flow area is minimized, in which the number of the second overlapping portions is one.

FIG. 3 is an exploded view of two impeller bodies of an embodiment of the present application, in which the number of second overlap portions is one;

FIG. 4 is a cross-sectional view taken at location A-A of FIG. 1;

FIG. 5 is an exploded view of two impeller bodies according to an embodiment of the present application, in which the number of second overlapping portions is two;

FIG. 6 is a schematic structural view of a mounting shaft according to an embodiment of the present application;

FIG. 7 is a schematic view of the relative arrangement of two bushings according to an embodiment of the present application;

FIG. 8 is a schematic structural view of a bushing according to an embodiment of the present application;

FIG. 9 is an enlarged view of FIG. 1 at location B showing the sealing boot;

fig. 10 is an enlarged view of fig. 1 at position B, without the gland;

fig. 11 is a schematic structural diagram of a sealing sleeve according to an embodiment of the present application.

Description of reference numerals: a flow channel 1; an impeller main body 2; a hub 21; a third shaft shoulder 211; a first blade 221; the first overlap portion 2211; a first stop table 2212; a second blade 222; the second overlap portion 2221; a second stop table 2222; a front cover plate 23; installing a shaft 3; an external spline 31; a first shaft section 32; a second shaft section 33; a shaft sleeve 4; the first sub-boss 41; a first shoulder 411; an internal spline 412; a sealing section 413; the second sub-boss 42; a second shoulder 421; a flat bond 5; a sealing sleeve 6; mounting the convex ring 61; a seal groove 7; an annular groove 71; a connecting mechanism 8; a stopper 9; shaft assembly 300.

Detailed Description

It should be noted that, in the present application, technical features in examples and embodiments may be combined with each other without conflict, and the detailed description in the specific embodiment should be understood as an explanation of the gist of the present application and should not be construed as an improper limitation to the present application.

In the description of the embodiments of the present application, the directions "inner" and "outer" are referred to the center line of rotation, radially toward the center line of rotation as "inner" and radially away from the center line of rotation as "outer".

It can be understood that the flow rate of the delivery pump is related to parameters such as power, pressure, and rotation speed, and in the related art, the flow rate adjustment mode of the delivery pump mainly changes the output power of the motor, and mainly achieves the purpose of adjusting the output power of the motor by adding a frequency converter in the driving circuit. The flow rate of the delivery pump is not only related to factors such as power and rotating speed, but also affected by the change of the size of the flow passage of the impeller assembly.

In view of this, the present disclosure provides a delivery pump, which includes an impeller assembly and a pump casing, wherein the impeller assembly is mounted on the pump casing, and the impeller assembly rotates around a rotation center line N to deliver fluid in the pump casing.

It will be appreciated that the impeller assembly rotates about the rotation centre line N and fluid within the pump casing is discharged from the outlet of the pump casing under the pumping action created by the rotation of the impeller assembly.

In one embodiment, the fluid pumped by the delivery pump may be water.

In one embodiment, the transfer pump may be a centrifugal pump.

In one embodiment, the centrifugal pump may be a single stage double suction centrifugal pump. Single stage double suction centrifugal pumps are also known as split pumps.

Referring to fig. 1 to 5, the impeller assembly of the embodiment of the present application includes a rotation center line N and a flow channel 1 located around the rotation center line N, the impeller assembly includes two impeller bodies 2, each impeller body 2 rotates around the rotation center line N, the two impeller bodies 2 are arranged oppositely along an extending direction of the rotation center line N, the two impeller bodies 2 surround the flow channel 1, and the two impeller bodies 2 change an area of the flow channel 1 by being close to or far from each other to adjust a flow rate of the flow channel 1. In such a structural form, when the two impeller main bodies 2 are close to each other, the width of the flow channel 1 is reduced, and correspondingly the flow area of the flow channel 1 is reduced, so that the flow rate of the delivery pump can be reduced to a certain extent under the condition that the rotating speed of the impeller main bodies 2 is basically unchanged; when the two impeller bodies 2 are far away from each other, the width of the flow channel 1 is increased, and accordingly the flow area of the flow channel 1 is increased, and under the condition that the rotating speed of the impeller bodies 2 is basically unchanged, the flow rate of the delivery pump can be increased to a certain extent. Through the mutual approaching and the mutual keeping away from of two impeller main parts 2, the flow area of the flow channel 1 is changed, thereby adjusting the flow of the delivery pump, and in the flow adjusting process of the delivery pump, the rotating speed of the impeller main part 2 does not need to be changed, so that a frequency converter does not need to be added in a power grid, the flow adjusting cost of the delivery pump is reduced, and the pollution of the delivery pump to the power grid in the flow adjusting process is reduced.

It can be understood that, the rotating speed of the impeller main body 2 is unchanged, the flow rate of the flow channel 1 is changed, the output power of the motor for driving the impeller main body 2 to rotate is correspondingly changed, and a frequency converter is not required to change the output power of the motor.

It can be understood that the flow area of the flow channel 1 is increased, the volume of the corresponding flow channel 1 is increased, the flow area of the flow channel 1 is decreased, and the volume of the corresponding flow channel 1 is decreased.

In one embodiment, the width direction of the flow channel is the extending direction of the rotation center line N.

In one embodiment, the delivery pump further comprises two traction mechanisms, each traction mechanism is connected with a corresponding impeller body, and each traction mechanism drives the corresponding impeller body to move so as to enable the two impeller bodies to approach or move away from each other. According to the structure form, the impeller main body is driven to move by the traction mechanism so as to realize flow regulation.

In one embodiment, each impeller body 2 may be integrally formed.

In an embodiment, the impeller body 2 is manufactured by casting, and the impeller body 2 is processed by casting, so that the impeller body 2 with a complex shape can be conveniently processed and manufactured.

In one embodiment, the impeller body 2 includes a plurality of sub-impellers arranged in the circumferential direction of the rotation center line N.

In one embodiment, referring to fig. 2 to 5, the impeller body 2 includes blades, and the blades of the two impeller bodies 2 are partially overlapped to limit the fluid in the flow passage 1 from leaking between the blades of the two impeller bodies 2. In such a structure, the blades of the two impeller bodies 2 are partially overlapped, so that the flow of the fluid in the flow channel 1 is limited in the process that the two impeller bodies 2 are close to or far away from each other to adjust the flow rate of the delivery pump, the possibility that the fluid in the flow channel 1 is thrown out from between the two blades under the action of the centrifugal force of the blades is reduced, the possibility that the fluid in the flow channel 1 leaks from between the blades of the two impeller bodies 2 can be reduced to a certain extent, and the pumping efficiency is improved.

It will be appreciated that when the vanes of the two impeller bodies 2 are partially stacked, there may be no seal between the vanes of the two impeller bodies 2 and a small amount of fluid may leak out from between the vanes of the two impeller bodies 2.

In one embodiment, referring to fig. 2 to 5, the blades of the two impeller bodies 2 are connected in a sealing manner to limit the fluid in the flow passage 1 from leaking between the blades of the two impeller bodies 2. With the structure, the fluid in the flow channel 1 basically cannot leak out from between the blades of the two impeller bodies 2 through the sealed connection of the blades of the two impeller bodies 2, and the pumping efficiency is improved.

It can be understood that when the blades of the two impeller bodies 2 are sealingly connected, since the gap between the blades of the two impeller bodies 2 is sealed, the fluid in the flow passage 1 does not substantially flow out from between the blades of the two impeller bodies 2, thereby preventing the fluid from leaking.

In an embodiment, referring to fig. 2 to 5, the impeller body 2 further includes a hub 21 and a front cover plate 23, the hub 21, the blades and the front cover plate 23 of the two impeller bodies 2 enclose the flow channel 1, and the blades of the two impeller bodies 2 are partially overlapped to prevent the fluid in the flow channel 1 from leaking between the blades of the two impeller bodies 2.

In one embodiment, referring to fig. 2 to 5, the front cover plate 23 surrounds the hub 21, wherein the front cover plate 23 of one impeller body 2 is located on a side of the corresponding blade facing away from the other impeller body 2.

In one embodiment, the hub 21, blades and front cover 23 are interconnected.

In one embodiment, the hub 21, blades and front cover 23 are integrally formed.

In one embodiment, hub 21, blades, and front cover plate 23 are welded.

In one embodiment, referring to fig. 2 to 5, at one end of the blades close to the hub 21 along the radial direction of the hub 21, the blades are respectively connected with the front cover plate 23 and the hub 21, and at this position, the blades of the two impeller bodies 2 are not hermetically connected with each other, but are respectively connected with the corresponding hub 21. On the outside of the hub 21, i.e. on the side of the hub 21 facing away from the centre line of rotation N, the blades are no longer connected to the hub 21, in which position they are connected to the respective front cover plate 23, the blades of the two impeller bodies 2 being partly superposed on one another.

In an embodiment, referring to fig. 2 to 5, in the two impeller bodies 2, the vane of one impeller body 2 is the first vane 221, the vane of the other impeller body 2 is the second vane 222, and the first vane 221 and the second vane 222 are partially overlapped.

In one embodiment, referring to fig. 2 to 5, the first blade 221 is formed with a first overlapping portion 2211, the second blade 222 is formed with a second overlapping portion 2221, and the first overlapping portion 2211 and the second overlapping portion 2221 are overlapped to limit the fluid in the flow passage 1.

In one embodiment, referring to fig. 2 to 5, the first vane 221 further forms a first stop boss 2212, and the first stop boss 2212 is located at an end of the first stacking portion 2211 facing away from the second vane 222 along the rotation center line N. The second blade 222 is further formed with a second stop table 2222, and the second stop table 2222 is located at an end of the second stacking portion 2221 facing away from the first blade 221 along the rotation center line N. In the radial direction of the rotation center line N, the second overlap portion 2221 abuts on the side of the first overlap portion 2211 facing the first stop table 2212, and the first overlap portion 2211 abuts on the side of the second overlap portion 2221 facing the second stop table 2222, so that the first overlap portion 2211 and the second overlap portion 2221 overlap each other. The formation of the folded gaps between the first and second stop stages 2212 and 2222 and the first and second stacks 2211 and 2221 is beneficial to prevent fluid from leaking out of the gap between the first and second stacks 2211 and 2221.

In one embodiment, referring to fig. 2 to 5, the first stacking portion 2211 is provided with a first stop 2212 along at least one radial side of the rotation center line N.

In one embodiment, referring to fig. 5, the second stacking portions 2221 are disposed on both sides of the first stacking portion 2211 along the radial direction of the rotation center line N, and the first stacking portion 2211 abuts against the second stacking portions 2221 on both sides along the radial direction of the rotation center line N, so that the first stacking portion 2211 and the second stacking portion 2221 are stacked in multiple layers. With such a configuration, the first and second overlaps 2211 and 2221 are stacked on each other in multiple layers, which is advantageous for preventing fluid from leaking out of the gap between the first and second overlaps 2211 and 2221.

In one embodiment, the first stacking portion 2211 is provided with first stopping steps 2212 at both sides in the radial direction of the rotation center line N. Both sides of the first overlapping portion 2211 in the radial direction of the rotation center line N are provided with second overlapping portions 2221, and the first overlapping portion 2211 abuts against the second overlapping portions 2221 in the radial direction of the rotation center line N. With such a structure, the gap formed between the first stop table 2212 and the first and second stacks 2211 and 2221 is bent more times, which is beneficial for preventing the fluid from flowing out from the gap between the first and second stacks 2211 and 2221 and leaking out.

In one embodiment, the first vane 221 and the second vane 222 may be sealed by a seal therebetween.

In one embodiment, the impeller assembly further includes a shaft assembly 300, the impeller body 2 is sleeved on the shaft assembly 300, and the impeller body 2 can move along the axial direction of the shaft assembly 300. In this configuration, the impeller main body 2 is supported by the shaft assembly 300, and the impeller main body 2 moves on the shaft assembly 300 to achieve adjustment of the flow area of the flow passage.

In one embodiment, referring to fig. 1, 6-8, the shaft assembly 300 further includes a mounting shaft 3 and a shaft sleeve 4. Installation axle 3 is located to the axle sleeve 4 cover, and axle sleeve 4 can be followed installation axle 3's axial displacement, and corresponding axle sleeve 4 is located to 2 covers of at least one impeller main part, and axle sleeve 4 is used for driving impeller main part 2 along axial displacement for installation axle 3. According to the structure, the installation shaft 3 can be installed on the pump shell, the impeller main bodies 2 are supported by the installation shaft 3, the impeller sleeves are arranged on the corresponding shaft sleeves 4, the shaft sleeves 4 move on the installation shaft 3 to drive the impeller main bodies 2 arranged on the shaft sleeves 4 to move, so that the two impeller main bodies 2 are close to and far away from each other, and the purpose of adjusting the flow area of the flow channel 1 and further adjusting the flow of the delivery pump is achieved. Shaft sleeve 4 drives impeller main part 2 and follows axial displacement for installation axle 3, and impeller main part 2 can not take place to remove for shaft sleeve 4 basically, can not have the friction between impeller and the shaft sleeve 4 basically, and it is close to each other or keep away from to realize two impeller main parts 2 for installation axle 3 removal through shaft sleeve 4, and in the adjustment process, the friction mainly takes place between shaft sleeve 4 and installation axle 3, and the impeller does not have wearing and tearing hardly to the impeller has been protected betterly. On the other hand, even if the shaft sleeve 4 is damaged due to abrasion, only the shaft sleeve 4 needs to be replaced independently, the whole impeller main body 2 does not need to be replaced, and the maintenance cost of the delivery pump is reduced.

In an embodiment, referring to fig. 1, fig. 6 to fig. 8, the number of the shaft sleeves 4 is two, the two shaft sleeves 4 are arranged oppositely along the axial direction of the mounting shaft 3, each impeller main body 2 is sleeved on the corresponding shaft sleeve 4, and the shaft sleeves 4 are used for driving the corresponding impeller main body 2 to move axially relative to the mounting shaft 3.

In one embodiment, the wear resistance of the sleeve 4 is higher than the wear resistance of the impeller body 2. Through the better axle sleeve 4 of wearability and the friction of installation axle 3, be favorable to reducing the friction loss.

In one embodiment, the shaft sleeve 4 is used to limit the movement of the impeller body 2 relative to the shaft sleeve 4, so that the shaft sleeve 4 drives the corresponding impeller body 2 to move axially relative to the mounting shaft 3.

In one embodiment, the sleeve 4 is made by forging. Through the mode of forging with the formula for the material of axle sleeve 4 is more compact, and the wearability is better.

In one embodiment, the forged sleeve 4 has a higher wear resistance than the cast impeller body 2, with substantially the same material.

It should be noted that the wear resistance refers to the ability to resist mechanical wear. The wear resistance of the bushing 4 is higher than that of the impeller body 2, i.e. the ability of the bushing 4 to resist wear is higher than that of the impeller body 2 to resist mechanical wear.

It will be appreciated that under substantially the same conditions, the amount of wear of the sleeve 4 is less than that of the impeller.

In one embodiment, shaft sleeve 4 may not be provided, shaft assembly 300 is an installation shaft, and impeller main body 2 is sleeved on the installation shaft and directly contacts with the installation shaft. Illustratively, the impeller body 2 is keyed to the mounting shaft.

It will be appreciated that the impeller assembly may be provided without the shaft assembly 300 and in one embodiment the hub 21 of the impeller body 2 may be supported on a pump casing to which the hub 21 is rotatably connected. The motor drives the hub 21 to rotate through a belt drive or a gear drive. With this structure, the hub 21 of the impeller main body 2 is supported on the pump casing, and the shaft assembly 300 is not required to support the impeller main body 2.

In one embodiment, the mounting shaft 3 is keyed to the bushing 4. Like this structural style, because the rotation of axle sleeve 4 for installation axle 3 is restricted, the axle sleeve 4 that two impeller main parts 2 correspond will follow installation axle 3 synchronous rotation, because axle sleeve 4 restriction impeller main part 2 removes for axle sleeve 4, two impeller main parts 2 synchronous rotations under the drive of installation axle 3 and corresponding axle sleeve 4, be favorable to impeller main part 2 pump fluid, prevent that two impeller main parts 2 from misplacing at the rotation in-process.

In one embodiment, the sleeve 4 is also rotatable with respect to the mounting shaft 3. Utilize installation axle 3 to support axle sleeve 4, installation axle 3 is installed on the pump case itself and is not transmitted power, thereby the motor drives axle sleeve 4 through belt drive or gear drive etc. and rotates and drive the impeller main part 2 of cover on axle sleeve 4 and rotate.

In one embodiment, the mounting shaft 3 is rotatably connected to the pump housing.

In one embodiment, when the mounting shaft 3 is rotatably connected to the pump housing, the driving member can drive the mounting shaft 3 to rotate.

In one embodiment, when the mounting shaft 3 is mounted on the pump casing to limit the rotation of the mounting shaft 3 relative to the pump casing, the shaft sleeve 4 rotates relative to the mounting shaft 3, and the motor drives the shaft sleeve 4 to rotate through belt transmission or gear transmission and the like, so as to drive the impeller main body 2 sleeved on the shaft sleeve 4 to rotate.

In an embodiment, referring to fig. 7 and 8, the shaft sleeve 4 includes a first sub-shaft sleeve 41 and a second sub-shaft sleeve 42, the first sub-shaft sleeve 41 is sleeved on the mounting shaft 3, the first sub-shaft sleeve 41 can move along the axial direction of the mounting shaft 3 and rotate along with the mounting shaft 3, the corresponding impeller main body 2 is sleeved on the first sub-shaft sleeve 41 so that the corresponding impeller main body 2 rotates along with the first sub-shaft sleeve 41, and a first shoulder 411 is formed at one end of the first sub-shaft sleeve 41. The second sub-sleeve 42 is sleeved on the mounting shaft 3, the second sub-sleeve 42 can move along the axial direction of the mounting shaft 3, the second sub-sleeve 42 is mounted at one end of the first sub-sleeve 41, which is away from the first shoulder 411, the second sub-sleeve 42 is formed with a second shoulder 421, and an area between the first shoulder 411 and the second shoulder 421 is used for at least partially accommodating the corresponding impeller main body 2 to limit the axial movement of the corresponding impeller main body 2 along the mounting shaft 3. With the structure, when the impeller body 2 needs to be installed, the impeller body 2 can be sleeved on the first sub-shaft sleeve 41, and then the second sub-shaft sleeve 42 is connected with the first sub-shaft sleeve 41, because the first shaft shoulder 411 and the second shaft shoulder 421 limit the axial movement of the impeller body 2 along the installation shaft 3, the impeller body 2 can rotate along with the first sub-shaft sleeve 41, and therefore, almost no friction exists between the impeller body 2 and the first sub-shaft sleeve 41, and almost no friction exists between the impeller body 2 and the second sub-shaft sleeve 42, so that the impeller body 2 can be effectively protected, and the abrasion of the impeller body 2 is reduced. Through the connection of the first sub-bushing 41 and the second sub-bushing 42 and the mutual matching of the first shoulder 411 and the second shoulder 421, the impeller main body 2 can be conveniently installed on the bushing 4, and the purpose of limiting the movement of the impeller main body 2 relative to the bushing 4 is achieved.

In one embodiment, referring to fig. 9 and 10, the impeller main body 2 abuts against the first shoulder 411 and the second shoulder 421 respectively.

In one embodiment, referring to fig. 7-10, the area between the first shoulder 411 and the second shoulder 421 is configured to at least partially receive the corresponding hub 21 to limit axial movement of the corresponding hub 21 along the mounting shaft 3, and thus axial movement of the impeller body 2 along the mounting shaft 3.

In one embodiment, referring to fig. 9 and 10, the hub 21 abuts against the first shoulder 411 and the second shoulder 421 respectively.

In an embodiment, referring to fig. 9 and 10, a third shoulder 211 abutting against the second shoulder 421 is formed on the inner side of the hub 21.

In one embodiment, the first sub-sleeve 41 and the second sub-sleeve 42 are detachably coupled. With the structure, the impeller body 2 can be conveniently mounted on the shaft sleeve 4 and also can be conveniently dismounted from the shaft sleeve 4, and the impeller body 2 and the shaft sleeve 4 are maintained.

In an embodiment, the first sub-sleeve 41 and the second sub-sleeve 42 may be detachably connected by a screw or a snap.

In one embodiment, the first sub-sleeve 41 and the second sub-sleeve 42 are welded.

In one embodiment, the impeller is sleeved on the first sub-sleeve 41, and the impeller is welded to the first sub-sleeve 41.

In one embodiment, when the impeller is welded to the first sub-sleeve 41, the second sub-sleeve 42 may not be provided.

In one embodiment, the first sub-sleeve 41 is keyed to the impeller body 2 such that the impeller body 2 follows the rotation of the first sub-sleeve 41.

In one embodiment, referring to fig. 1, 6-10, the impeller assembly further includes a flat key 5.

In one embodiment, referring to fig. 1, 6-10, an inner spline 412 is formed on the inner side of each first sub-sleeve 41, and the inner spline 412 of each first sub-sleeve 41 is engaged with the corresponding outer spline 31 on the mounting shaft 3. In such a structural form, the internal spline 412 and the external spline 31 are engaged to enable the first sub-sleeve 41 and the mounting shaft 3 to form a spline connection, torque needs to be transmitted between the first sub-sleeve 41 and the mounting shaft 3, the first sub-sleeve 41 needs to move along the axial direction of the mounting shaft 3, the first sub-sleeve 41 and the mounting shaft 3 are connected through the spline, the contact area of the first sub-sleeve 41 and the mounting shaft 3 for transmitting torque is large, pressure caused by torque on the contact surface is small, and abrasion caused by relative movement between the first sub-sleeve 41 and the mounting shaft 3 is reduced.

In one embodiment, the outer side of the first sub-sleeve 41 is fixedly connected to the impeller body 2. The impeller body 2 is fixedly connected with the impeller body 2 through the outer side of the first sub-sleeve 41, so that the impeller body 2 rotates along with the first sub-sleeve 41.

In one embodiment, the outer side of the first sub-sleeve 41 is fixedly connected with the impeller body 2 through a flat key connection or a spline connection.

In one embodiment, the outer side of the first sub-sleeve 41 is fixedly connected with the impeller main body 2 by interference fit.

In one embodiment, the outer side of the first sub-sleeve 41 is fixedly connected with the impeller main body 2 by brazing welding.

Through the difference of the key connection type at different positions of the first sub-shaft sleeve 41, the abrasion of the first sub-shaft sleeve 41 is reduced, and the connection mode of the first sub-shaft sleeve 41 and the impeller main body 2 is simpler.

In one embodiment, the first subshaft 41 is connected to the mounting shaft 3 by a flat key.

In one embodiment, the first subshaft 41 is splined to the impeller body 2.

In one embodiment, referring to fig. 6, the mounting shaft 3 includes a second shaft section 33 and two first shaft sections 32, each of the first shaft sections 32 corresponds to a first sub-sleeve 41 and a second sub-sleeve 42, and the first sub-sleeve 41 and the second sub-sleeve 42 can move along the axial direction of the corresponding first shaft section 32. The second shaft section 33 is connected between the two first shaft sections 32, the two first sub-shaft sleeves 41 are all sleeved on the second shaft section 33, the diameter of the second shaft section 33 is larger than that of the first shaft section 32, and two ends of the second shaft section 33 can be respectively abutted against the end portions of the corresponding internal splines 412 to position the corresponding first sub-shaft sleeves 41. In such a structure, because the diameters of the two first shaft sections 32 at the two ends of the second shaft section 33 are smaller than the diameter of the second shaft section 33, the internal spline 412 of the first sub-shaft sleeve 41 sleeved on the first shaft section 32 can be abutted with one end corresponding to the second shaft section 33 to position the first sub-shaft sleeve 41, and the positioning of the impeller main body 2 is indirectly realized, so that the two impeller main bodies 2 supported on the mounting shaft 3 can be prevented from being excessively deviated from one end of the mounting shaft 3 in the flow rate adjusting process to a certain extent, which is beneficial to better pumping fluid, and the overall load of the delivery pump is more uniform.

It should be noted that the second shaft section 33 is only abutted and positioned with the two first sub-shaft sleeves 41 in the state that the two first sub-shaft sleeves 41 are closest to each other, and after the positioning is completed, the two first sub-shaft sleeves 41 can be kept to synchronously move along the directions deviating from each other, so as to prevent the two impeller main bodies 2 sleeved on the corresponding first sub-shaft sleeves 41 from excessively deviating to one end of the mounting shaft 3.

In one embodiment, the first shaft section 32 and the second shaft section 33 may be integrally formed.

In an embodiment, the first sub-sleeve 41 may be sleeved on the first shaft section 32 but not on the second shaft section 33, and an end of the first sub-sleeve 41 abuts against the second shaft section 33 to position the second shaft section 33 on the first sub-sleeve 41.

It is understood that the fluid in the flow passage 1 may infiltrate between the two impeller bodies 2 and the two first sub-bushings 41, and the fluid infiltrating between the two first sub-bushings 41 may flow toward the second shaft section 33 and leak outward through the two first shaft sections 32. In one embodiment, referring to fig. 9 and 10, the second shaft section 33 is hermetically connected to both of the first sub-bushings 41 to prevent the fluid in the flow channel 1 from leaking between the second shaft section 33 and the first sub-bushings 41. With such a structure, the two first sub-bushings 41 are hermetically connected with the second shaft section 33, and the gap between the two first sub-bushings 41 and the space where the two first shaft sections 32 are located are separated, so that the liquid seeping into the flow channel 1 between the two first sub-bushings 41 is prevented from leaking to the space where the two first shaft sections 32 are located through the gap between the first sub-bushings 41 and the second shaft section 33, and the pumping efficiency can be improved to a certain extent.

In one embodiment, the first subshaft sleeve 41 is sealed from the second shaft section 33 by means of a respective seal.

In one embodiment, referring to fig. 6, the mounting shaft 3 is formed with external splines 31.

In one embodiment, referring to fig. 6, the external splines 31 are formed on the first shaft section 32. Each first shaft section 32 is formed with an external spline 31.

In an embodiment, referring to fig. 1, fig. 7 to fig. 10, the first shoulder 411 is located at an end of the corresponding impeller body 2 facing the other impeller body 2, and the second shoulder 421 is located at an end of the corresponding impeller body 2 facing away from the other impeller body 2; the two first sub-sleeves 41 are located between the two second sub-sleeves 42 in the axial direction of the mounting shaft 3. In such a structure, the two first sub-bushings 41 are located between the two second sub-bushings 42, so that the second sub-bushings 42 are located at the ends of the two first sub-bushings 41 away from each other, because the second shoulder 421 is located at the end of the corresponding impeller body 2 away from the other impeller body 2, the second sub-bushings 42 are located at the ends of the two first sub-bushings 41 away from each other, the positions of the second sub-bushings 42 are not shielded by the impeller body 2, so that an operator can assemble and disassemble the second sub-bushings 42 more conveniently, the operator only needs to screw or unscrew the threads of the second sub-bushings 42 to assemble and disassemble the first sub-bushings 41 and the second sub-bushings 42, the impeller rotates along with the first sub-bushings 41, the torque is mainly transmitted through the first sub-bushings 41, the second sub-bushings 42 can not transmit the impeller torque, and therefore, when the second sub-bushings 42 are screwed or unscrewed, the rotation of the second sub-sleeve 42 can not drive the impeller main body 2 to rotate, so that the dismounting operation of the second sub-sleeve 42 is simple.

In one embodiment, the first shoulder 411 is located at an end of the corresponding impeller body 2 facing away from the other impeller body 2, and the second shoulder 421 is located with an end of the corresponding impeller body 2 facing toward the other impeller body 2. The two second sub-sleeves 42 are located between the two first sub-sleeves 41 in the axial direction of the mounting shaft 3.

It can be understood that the torque of the impeller acting on the first sub-sleeve 41 through the flat key 5 is a first torque, and the torque of the mounting shaft 3 acting on the first sub-sleeve 41 through the internal spline 412 and the external spline 31 is a second torque, and the first torque and the second torque are opposite in direction, and both the first torque and the second torque act on the first sub-sleeve 41 to deform the first sub-sleeve 41 to some extent. In one embodiment, referring to fig. 1, 6-10, the flat key 5, the internal spline 412 and the external spline 31 are located between the first shoulder 411 and the second shoulder 421 along the axial direction of the mounting shaft 3. In this way, since the impeller main body 2 is located between the first shoulder 411 and the second shoulder 421, the flat key 5 is located between the first shoulder 411 and the second shoulder 421 so that the first sub-sleeve 41 can be connected with the impeller main body 2 through the flat key 5. The flat key 5 for connecting the first sub-sleeve 41 and the impeller body 2, and the internal spline 412 which are engaged with each other are located between the first shoulder 411 and the second shoulder 421, and the position where the internal spline 412 and the external spline 31 are engaged with each other is closer to the position where the first sub-sleeve 41 and the impeller body 2 are connected by the flat key 5, and the distance between the first torque and the second torque is closer in the axial direction of the mounting shaft 3. Keeping the torsion load unchanged, the first sub-sleeve 41 will form substantially the same strain under the action of torsion, and the torsion angle formed by the first sub-sleeve 41 under the action of torsion is smaller due to the closer distance between the first torque and the second torque. Therefore, the arrangement of the flat key 5, the inner spline and the outer spline 31 reduces the degree of deformation of the first sub-sleeve 41 to some extent.

It should be noted that the shear strain formed by the first torque and the second torque acting on the first sub-sleeve 41 is inversely proportional to the distance between the first torque and the second torque, the shear strain formed by the first torque and the second torque acting on the first sub-sleeve 41 is proportional to the torsion angle formed by the first sub-sleeve 41 under the torsion action, the shear strain is proportional to the shear stress, and the shear stress is proportional to the torque.

Illustratively, the position where the first sub-sleeve 41 acts on is approximately at the position where the first sub-sleeve 41 is connected with the impeller body 2 by the flat key 5, and the position where the second torque acts on the first sub-sleeve 41 is approximately at the position where the internal spline 412 and the external spline 31 are engaged. The first torque is a, the second torque is B, the magnitude of the first torque and the magnitude of the second torque are kept unchanged, the shear strain formed by the first sub-sleeve 41 under the action of the first torque and the second torque is basically unchanged, the closer the position of the first torque acting on the first sub-sleeve 41 is to the position of the second torque acting on the first sub-sleeve 41, the smaller the torsion angle formed by the first sub-sleeve 41 under the action of the torsion, the farther the position of the first torque acting on the first sub-sleeve 41 is from the position of the second torque acting on the first sub-sleeve 41, and the larger the torsion angle formed by the first sub-sleeve 41 under the action of the torsion.

In one embodiment, referring to fig. 8, the first sub-sleeve 41 is formed with a sealing section 413, the sealing section 413 is located between the internal splines 412 of the two first sub-sleeves 41, the sealing section 413 is sleeved on the second shaft section 33, the sealing section 413 is connected to the second shaft section 33 in a sealing manner, and the second shaft section 33 is located in the sealing section 413 and abuts against the internal splines 412 to position the first sub-sleeve 41.

In one embodiment, the first shoulder 411 is formed on the sealing section 413.

In one embodiment, the first subshaft 41 may be provided without internal splines 412 and the second subshaft 42 may form internal splines 412 that mesh with external splines 31 on the mounting shaft 3.

In one embodiment, the internal spline 412 on the second sub-sleeve 42 may be located on a side of the second shoulder 421 facing away from the first sub-sleeve 41.

In an embodiment, referring to fig. 1 to 3 and fig. 9 to 11, the impeller assembly further includes a sealing sleeve 6, the sealing sleeve 6 is located at one end of the two impeller bodies 2, the shaft sleeve 4 and the corresponding impeller body 2 are sealed by the sealing sleeve 6 to prevent the fluid in the flow channel 1 from leaking between the two impeller bodies 2, and the sealing sleeve 6 is disposed across the shaft sleeve 4 to prevent the fluid in the flow channel 1 from leaking between the two shaft sleeves 4. In such a structure, the impeller body 2 and the shaft sleeve 4 are sealed by the sealing sleeve 6, so that the fluid in the flow passage 1 is prevented from leaking, and the pumping efficiency of the delivery pump is improved.

In one embodiment, referring to fig. 1 to 3 and fig. 9 to 11, one end of each of the two impeller bodies 2 close to each other is enclosed by a sealing groove 7, the sealing sleeve 6 is installed in the sealing groove 7, the sealing groove 7 has two annular grooves 71 oppositely arranged along the axial direction of the mounting shaft 3, the sealing sleeve 6 is formed with two mounting convex rings 61 oppositely arranged along the axial direction of the mounting shaft 3, each mounting convex ring 61 is located in a corresponding annular groove 71, and each mounting convex ring 61 is in sealing abutment with the corresponding shaft sleeve 4 and the impeller body 2 respectively to restrain the mounting convex ring 61 in the annular groove 71. According to the structure, the annular groove 71 is matched with the mounting convex ring 61, so that the mounting convex ring 61 is respectively abutted against the shaft sleeve 4 and the impeller main body 2, on one hand, the mounting convex ring 61 of the sealing sleeve 6 is clamped in the annular groove 71, the sealing sleeve 6 is firmly mounted, on the other hand, good sealing is formed between the sealing sleeve 6 and the shaft sleeve 4 and between the sealing sleeve 6 and the impeller main body 2, and fluid leakage in the flow channel 1 is prevented.

In one embodiment, the ends of the two hubs 21 adjacent to each other form a seal groove 7.

In one embodiment, referring to fig. 1 and 7, the impeller assembly further includes a connecting mechanism 8 connected to the shaft sleeve 4, wherein the connecting mechanism 8 is capable of rotating around the shaft sleeve 4.

In one embodiment, the pulling mechanism is coupled to the coupling mechanism 8 to drive the sleeve 4 in axial movement along the mounting shaft 3. The traction mechanism is indirectly connected with the impeller main body 2 through the connecting mechanism 8 and the shaft sleeve 4.

It can be understood that the traction mechanism drives the shaft sleeve 4 to move through the connecting mechanism 8 so as to drive the impeller main body 2 sleeved on the shaft sleeve 4 to move, so that the impeller main bodies 2 are close to or far away from each other. Because coupling mechanism 8 can rotate around axle sleeve 4, at axle sleeve 4 rotation in-process, coupling mechanism 8 can not rotate along axle sleeve 4, through the axial displacement of drive coupling mechanism 8 and axle sleeve 4 along installation axle 3 of drive mechanism, and drive mechanism can not rotate along axle sleeve 4, can prevent to a certain extent that drive mechanism from appearing pipeline or circuit winding's problem.

In one embodiment, the traction mechanism may be an oil cylinder, an air cylinder or an electric push rod.

In an embodiment, the traction mechanism may also be directly connected to the impeller body 2.

In one embodiment, the connecting mechanism 8 may be a bearing, an inner ring of the bearing is sleeved on the shaft sleeve 4, and an outer ring of the bearing rotates relative to the shaft sleeve 4.

In one embodiment, the inner race of the bearing may be welded to the sleeve 4.

In one embodiment, the inner race of the bearing may abut the stop 9 to limit axial movement of the bearing relative to the sleeve 4 along the mounting shaft 3.

In one embodiment, the connection mechanism 8 may not be provided, and the traction mechanism may be configured without an external pipeline or an external circuit. For example, drive mechanism can be for the electric putter from electrified pond, is connected electric putter's one end and installation axle 3, and electric putter's the other end is connected with axle sleeve 4, and when axle sleeve 4 followed installation axle 3 and rotates, electric putter also can follow installation axle 3 and rotate, because electric putter is from taking the battery, does not need external electric wire nor external pipeline, and electric putter follows the installation axle 3 pivoted in-process and can not appear pipeline or circuit winding's problem basically. The axial movement of the shaft sleeve 4 on the mounting shaft 3 can be realized by pushing and pulling the shaft sleeve 4 by the electric push rod.

The various embodiments/implementations provided herein may be combined with each other without contradiction.

The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.