CN107339254B

CN107339254B - Water pump blade angle in-service adjusting device based on tooth difference driving

Info

Publication number: CN107339254B
Application number: CN201710467629.0A
Authority: CN
Inventors: 杨开好; 耿爱农; 李辛沫; 渠斌; 陈永盛; 袁龙刚; 王天雷; 王大承; 喻胜春; 胡顺彬; 杨大伟
Original assignee: Guangdong Hohai Pump Machinery Co ltd
Current assignee: Guangdong Hohai Pump Machinery Co ltd
Priority date: 2017-06-20
Filing date: 2017-06-20
Publication date: 2023-07-04
Anticipated expiration: 2037-06-20
Also published as: CN107339254A

Abstract

The invention belongs to the technical field of fluid machinery, and relates to a tooth difference driving type mechanical water pump blade angle adjusting device, which is characterized in that: the structure and the layout of the adjusting nut and the adjusting screw kinematic pair are innovated by adopting the tooth difference driving principle, so that the real-time in-service regulation and control of the attack angle of the water pump blade without stopping is realized. The bearing cover seat and the adjusting device body are adopted to jointly position and clamp the bearing mode of the adjusting nut, so that the supporting rigidity of the machine part is greatly improved, the transmission path of the load force is shortened, and the capability of the device for resisting the impact of the lifting shaft of the water pump is effectively enhanced; the special motor for blade adjustment of the traditional mechanical adjusting device is omitted, and the control link of the device is greatly simplified and optimized; the layout scheme of the all-in-one central clutch is adopted, so that the number of key parts is reduced, and the complexity of the device is reduced. The tooth difference driving type water pump blade angle adjusting device achieves the design targets of high working reliability, low production cost and compact overall size.

Description

Water pump blade angle in-service adjusting device based on tooth difference driving

Technical Field

The invention belongs to the technical field of fluid machinery, relates to a water pump, a water turbine and other fluid machinery devices which adopt paddles as tools to drive fluid media, in particular to an adjusting device capable of adjusting and controlling the angles of the blades of the water pump without stopping, and more particularly relates to a mechanical adjusting device which is driven by tooth difference and is used for adjusting and controlling the angles of the blades of the water pump in service.

Background

Both pumps and turbines require configuration of blades (also called paddles) to lift or deliver water to a target area. It is well known that the efficiency of the operation of such hydraulic devices is closely related to the angle of attack of their blades, i.e. "angle of attack". In general, there is and must be an optimum blade angle for the water pump to operate at which the water pump will achieve optimum water energy efficiency, corresponding to different operating conditions of the water pump. Undoubtedly, if the working angle of the blade can be regulated and controlled in real time according to different environmental backgrounds such as river and lake water level, seasonal variation, hydrologic conditions and the like, the output characteristic of the water pump discharge capacity can be optimized, and a large amount of electricity charge can be saved. Therefore, the existing large water pump and the unit thereof are provided with a device for adjusting the angle of the blade without exception, so that the angle of the blade can be adjusted and controlled according to specific conditions during the operation of the water pump to obtain optimal efficiency.

Currently, large water pumps commonly employ mechanical adjustment devices to implement non-stop blade angle adjustment operations, i.e., to change the working angle of the blade in service without stopping the water pump. To achieve this, it is conventional practice to employ a special adjusting motor and speed reducing mechanism, to drive a nut screw pair, to drive an adjusting lever coupled to the pump blade by axial displacement of the nut screw by-product, and to adjust the angle of attack of the pump blade by the adjusting lever. The advantages of such a mechanical adjusting device are obvious, on the one hand, it can realize self-locking and has good performance of locking the blade angle, and on the other hand, the process of adjusting the blade angle is very stable and accurate. As a result, mechanical blade angle adjustment devices have been used until now, and have seen a large market share, especially in large water pumps with impeller diameters of 1.5m to 3.1 m.

However, the conventional mechanical adjusting device must use a special adjusting motor as the actuating power of the adjusting device, and the defects and hidden troubles caused by the fact that the conventional mechanical adjusting device are very obvious are mainly that: (1) the adjusting device is huge after the adjusting motor is adopted, and the adjusting motor is known to occupy a certain space, so that the size of the traditional mechanical adjusting device is quite huge, and the size of the traditional mechanical adjusting device is higher than the size of the motor (about one fifth of the height of the whole device) in the height direction, so that the device is not compact enough, and the lifting, mounting and maintenance of the device are difficult; (2) the power receiving system of the regulating device becomes more complex after the regulating motor is adopted, the regulating motor needs to be independently supplied with power due to the existence of the regulating motor, the extra power supply and the power receiving system lead to the remarkable increase of the control links of the mechanism, and particularly for the regulating device of a follow-up motor type, the main body of the motor always rotates along with the water pump, so that the power receiving mode of the electric brush and the power receiving ring is required to be adopted, so that the reliability of power supply is poor; (3) the capacity of the adjusting device for resisting the shaft lifting impact of the water pump can be obviously reduced after the adjusting motor is adopted, and the cover is unreasonable in nut screw pair supporting structure of the mechanism due to the existence of the adjusting motor and the requirement of power transmission, so that the supporting links are more and the force transmission chain length is long, the integral rigidity of the device is very weak, in other words, the device is difficult to resist the shaft lifting impact force of the water pump, and the adjusting device has the hidden trouble of a "frying machine" caused by being jacked up and turned over.

In view of this, a differential gear driving type blade angle adjusting device is proposed by new Zhuang Zhengming (Japanese) et al, see "drainage and irrigation machinery" No. 4 of 1989, "modification of a vertical mixed flow pump to a fixed blade into an adjustable blade" (high-speed disc forest, chen Ji translation: 137may 1987, "Ebara Engineering Review"); the Chinese patent ZL99216481.8 (CN 2390020Y) also provides an automatic adjusting device for the blades of the rotating wheels of the water turbine and the water pump, which is similar to the principle of the automatic adjusting device. The solution proposed in the above document belongs to the category of typical mechanical adjusting devices, and starts from the fact that the blade angle is adjusted by means of a small tooth difference method and by means of the driving of the main motor of the water pump. The operating principle and the structural layout of the differential gear driving device are as follows: a main gear is driven by a rotor of a main motor of the water pump, a rolling gear is driven by the main gear, then an electromagnetic clutch associated with the rolling gear is utilized to select whether to drive a certain auxiliary shaft, a differential gear is linked on the auxiliary shaft, the differential gear has meshing relationship with a central gear arranged on an adjusting nut, when the central gear is driven to rotate, the central gear drives the adjusting nut to rotate and further drives an adjusting screw to generate axial movement, thereby the axial displacement of the adjusting screw drives an adjusting pull rod linked with a water pump blade, and finally the aim of changing the attack angle of the blade is achieved. In the above scheme, the two-way axial movement selection of the adjusting screw is realized by arranging two types of different specifications on the differential gears, wherein one differential gear has one more tooth number than the rolling gear and the other differential gear has one less tooth number than the rolling gear, correspondingly, at least two auxiliary shafts are required to be assembled, corresponding electromagnetic clutches are required to be arranged on the auxiliary shafts, and different tooth difference transmission paths are selected by controlling the electromagnetic clutches, so that the forward movement or the reverse movement of the adjusting screw is realized, and finally the increase or the decrease of the blade angle is finished. Needless to say, the advantages of the differential gear drive type blade angle adjustment device are very remarkable, and the special adjustment motor which is indispensable for the traditional mechanical adjustment device is completely abandoned, so that the compactness and the complexity of the device are greatly improved.

However, the differential gear driving type blade angle adjusting device provided in the above document has an incomparable advantage compared with the conventional mechanical adjusting device, but still has an imperfect place, and is characterized in that: (1) the provision of electromagnetic clutches on the auxiliary shafts leads to an increase in the production costs of the adjusting device, since the adjusting forces required when the lower water pumps, in particular large water pumps, change the blade angle are quite large, generally between 100KN and 700KN, the torque required for driving the adjusting nut to rotate is generally in the range of 120n.m to 680n.m, for which purpose a plurality of auxiliary shafts and a plurality of differential gears of the same regulation are necessary for jointly driving the central gear arranged on the adjusting nut, in other words the adjusting device must be provided with a plurality of electromagnetic clutches, not only the electromagnetic clutches required for regulating the forward rotation of the adjusting nut must be provided with more than two, but also the electromagnetic clutches required for regulating the reverse rotation of the adjusting nut must be provided with more than two, needless to say, the increase of the electromagnetic clutches necessarily increases the production costs of the adjusting device; (2) the arrangement of the electromagnetic clutch on the auxiliary shaft will lead to the reliability of the regulating device being lowered, as mentioned above, the scheme of arranging the electromagnetic clutch on the auxiliary shaft necessarily needs to be provided with a plurality of electromagnetic clutches, and the battery clutches must work in a coordinated and consistent manner, as is well known, the more the cooperative device units are, the higher the probability of failure, the more severe the working environment of the water pump can be, the higher the probability of failure of the electromagnetic clutch is increased, once one electromagnetic clutch fails, the differential gear responsible for the electromagnetic clutch will be out of operation without any load, at the moment, the load of the other differential gears which are still in operation will be suddenly increased, thereby the damage of the domino effect will not be a small probability event, in other words, the reliability of the regulating device will be lowered remarkably; (3) the provision of differential gears on the auxiliary shafts leads to an increase in the radial dimension of the adjustment device, as previously described, in which case a plurality of auxiliary shafts and a plurality of differential gears of the same type must be used to jointly drive the sun gears arranged on the adjustment nuts, and in order to counteract the radial forces derived from the respective meshing pairs, a plurality of auxiliary shafts, rolling gears, differential gears and electromagnetic clutches must be provided in a symmetrical arrangement, which in fact entails an increase in the radial dimension of the adjustment device, in other words, the differential gear-driven adjustment device provided in the above-mentioned document, although it can be made shorter in the height direction, has an increase in the radial dimension, which also means that there is a negative effect on the compact design of the device; (4) the provision of differential gears on the auxiliary shafts results in a great limitation of the reduction ratio of the regulating device, which is bound by the fact that the main motor of the water pump is of great constructional dimensions, the dimensions and number of teeth of the central gear of the regulating device must be far in excess of those of the differential gears, in other words the differential gears are actually small-sized gears (which is also one of the reasons that it is also necessary to arrange a plurality of differential gears in view of the strength), it is well known that the number of reduction ratios obtained by the differential gears is closely related to the number of teeth thereof, the reduction ratio achievable by the reduction ratio being greater the less the number of teeth of the differential gears, i.e. it means that it is difficult to arrange the tooth differences on the differential gears at this time to obtain a large number of reduction ratios, for example, in the case of the sun gear tooth number 80 (more teeth must be adopted due to the size restriction of the main motor of the water pump), the rolling gear tooth number 20, and the differential gear tooth number 19 or 21 (generally, in order to obtain the speed ratio effect to the maximum extent, the tooth difference is adopted as a design strategy of one tooth difference), the obtained reduction ratio is approximately 1:20 no matter the adjusting nut is driven forward or backward, and it is known that according to the existing water pump specification with the impeller diameter of 1.5m to 3.1m and the rotation speed range of the main motor of the water pump generally being 150r/min to 500r/min, the torque required for driving the adjusting nut to rotate is so large that the speed ratio generally needs to be 1:60 to 1:280, the basic tooth number of the differential gear is not too small, and the differential gear is arranged on the auxiliary shaft to hardly meet the reduction ratio plan of the adjusting device.

In summary, there is room for further improvement and lifting in the conventional mechanical water pump blade angle adjusting device, either in a conventional scheme using an adjusting motor or in a new scheme using a differential gear driving type.

Disclosure of Invention

Aiming at the problems of the prior mechanical water pump blade angle adjusting device, the invention provides a water pump blade angle in-service adjusting device based on tooth difference driving, which aims at: through improving the structural design and the overall arrangement of adjusting device core part, on the one hand improves adjusting device's resistance to water pump lift axle impact's ability, on the other hand effectively improves adjusting device's operational reliability, effectively reduces adjusting device's overall dimension simultaneously.

The object of the invention is achieved in that: the in-service water pump blade angle adjusting device based on tooth difference driving comprises an adjusting device body, an adjusting nut and an adjusting screw, wherein the adjusting device body can perform fixed-axis rotary motion around a rotary axis of the adjusting device body, the adjusting nut and the adjusting screw are coaxially arranged with the adjusting device body, the adjusting nut and the adjusting screw are matched in a spiral structure and form a spiral kinematic pair, and the adjusting nut can drive the adjusting screw to perform axial displacement motion; the method is characterized in that: the bearing seat is provided with a bearing seat, and the bearing seat cover is fixedly connected to the adjusting device body or is manufactured in an integrated structure with the adjusting device body; the adjusting nut is provided with an upper bearing surface and a lower bearing surface, wherein the lower bearing surface and the adjusting device body are in mutual bearing relation, the upper bearing surface and the bearing cover seat are in mutual bearing relation, the adjusting nut can only rotate around the axis of the adjusting device body and can not move along the axis of the adjusting nut under the joint constraint of the adjusting device body and the bearing cover seat, and the adjusting nut can have three running states of forward rotation, reverse rotation and static state relative to the adjusting device body; the device comprises a first central gear, a second central gear and a third central gear which are coaxially arranged with the adjusting device body, wherein the first central gear is connected to the adjusting device body in a matching way and receives the driving of the adjusting device body, or the first central gear and the adjusting device body are manufactured in an integrated structure; the relay rod is coaxially arranged with the adjusting device body, is matched with the adjusting nut or is manufactured in an integrated structure with the adjusting nut, and can drive the adjusting nut to operate; the auxiliary shafts are all rotatably mounted on the seat frame, a first gear is assembled on each auxiliary shaft, a second gear or/and a third gear is assembled on each auxiliary shaft, at least one auxiliary shaft is assembled with a second gear, at least one auxiliary shaft is assembled with a third gear, the first gear, the second gear and the third gear are all coaxially assembled on or integrally manufactured on the auxiliary shaft, wherein the first gear is in constant mesh with the first central gear, the second gear is in constant mesh with the second central gear, and the third gear is in constant mesh with the third central gear; the clutch II is matched with the second central gear and is responsible for determining whether the second central gear is in force transmission linkage with the relay rod, the clutch III is matched with the third central gear and is responsible for determining whether the third central gear is in force transmission linkage with the relay rod; the working states of the second clutch and the third clutch at the same moment are consistent, and one of the following three logic relations is needed to be taken and only taken: the second clutch is disconnected and the third clutch is also disconnected at the same time, the second clutch is connected but the third clutch is disconnected at the same time, the second clutch is disconnected but the third clutch is connected at the same time; the first gear is driven to operate by the first central gear and is driven to operate by a countershaft where the first gear is positioned, so that the countershaft drives a second gear and a third gear which are assembled on the countershaft to operate, then the second central gear and the third central gear are driven to operate respectively by the second gear and the third gear, when the second clutch is disconnected and the third clutch is also disconnected, the second central gear and the third central gear are both disconnected from a relay lever, when the second clutch is connected and the third clutch is disconnected, the relay lever is driven to operate only by the second clutch and the second central gear, and when the second clutch is disconnected and the third clutch is connected, the relay lever is driven to operate only by the third clutch and the third central gear; the first speed ratio is obtained by the ratio of the number of teeth of the first sun gear to the number of teeth of the first sun gear, the second speed ratio is obtained by the ratio of the number of teeth of the second sun gear to the number of teeth of the second sun gear, and the third speed ratio is obtained by the ratio of the number of teeth of the third sun gear, the product of the first speed ratio and the second speed ratio has a value greater than one, and the product of the first speed ratio and the third speed ratio has a value less than one.

Further, the above-mentioned adjusting device is provided with a sealing member which follows the adjusting screw rod and is in sealing engagement with the outer cylindrical surface of the adjusting nut or which is coupled to the adjusting nut and is in sealing engagement with the outer cylindrical surface of the polish rod of the adjusting screw rod.

Further, the relay rod is provided with a hollow hole, and is additionally provided with a displacement signal rod which penetrates through the hole of the relay rod, and the displacement signal rod is fixedly connected to the adjusting nut or is manufactured in an integrated structure with the adjusting nut.

Further, a main thrust bearing is arranged between the lower bearing surface of the adjusting nut bearing shaft shoulder and the adjusting device body.

Further, a radial positioning bearing and an axial supporting bearing are arranged between the seat frame and the adjusting device body.

Further, a lower positioning bearing and an upper positioning bearing are arranged between the adjusting nut and the adjusting device body.

A buffer gasket or/and a pre-tightening spring are arranged between the bearing cover seat and the bearing surface on the adjusting nut.

The adjusting device is provided with an emergency central gear and a reset gear, wherein the emergency central gear is coaxially matched and connected on the relay rod or the adjusting nut, and the reset gear can be meshed and matched with the emergency central gear.

The second clutch and the third clutch are both provided with oil separation covers.

The sum of the numbers of teeth of the first sun gear and the first gear is equal to the sum of the numbers of teeth of the second sun gear and the second gear, and is equal to the sum of the numbers of teeth of the third sun gear and the third gear.

The number of teeth of the second sun gear is one less than that of the first sun gear, and the number of teeth of the third sun gear is one more than that of the first sun gear.

The first gear, the second gear and the third gear have the same number of teeth.

The first sun gear, the second sun gear and the third sun gear have the same number of teeth.

The number of teeth of the second gear is one more than that of the first gear, and the number of teeth of the third gear is one less than that of the first gear.

The in-service water pump blade angle adjusting device based on tooth difference driving comprises an adjusting device body, an adjusting nut and an adjusting screw, wherein the adjusting device body can perform fixed-axis rotary motion around a rotary axis of the adjusting device body, the adjusting nut and the adjusting screw are coaxially arranged with the adjusting device body, the adjusting nut and the adjusting screw are matched in a spiral structure and form a spiral kinematic pair, and the adjusting nut can drive the adjusting screw to perform axial displacement motion; the method is characterized in that: the bearing seat is provided with a bearing seat, and the bearing seat cover is fixedly connected to the adjusting device body or is manufactured in an integrated structure with the adjusting device body; the adjusting nut is provided with an upper bearing surface and a lower bearing surface, wherein the lower bearing surface and the adjusting device body are in mutual bearing relation, the upper bearing surface and the bearing cover seat are in mutual bearing relation, the adjusting nut can only rotate around the axis of the adjusting device body and can not move along the axis of the adjusting nut under the joint constraint of the adjusting device body and the bearing cover seat, and the adjusting nut can have three running states of forward rotation, reverse rotation and static state relative to the adjusting device body; the device comprises a regulating device body, a first central synchronous wheel, a second central synchronous wheel and a third central synchronous wheel, wherein the first central synchronous wheel, the second central synchronous wheel and the third central synchronous wheel are coaxially arranged with the regulating device body, and the first central synchronous wheel is connected to the regulating device body in a matched mode and receives the driving of the regulating device body, or the first central synchronous wheel and the regulating device body are manufactured in an integrated structure; the relay rod is coaxially arranged with the adjusting device body, is matched with the adjusting nut or is manufactured in an integrated structure with the adjusting nut, and can drive the adjusting nut to operate; the device comprises a static seat frame and at least one auxiliary shaft, wherein all auxiliary shafts are rotatably arranged on the seat frame, a first synchronous wheel is assembled on each auxiliary shaft, a second synchronous wheel or/and a third synchronous wheel is assembled on each auxiliary shaft, at least one auxiliary shaft is assembled with a second synchronous wheel, at least one auxiliary shaft is assembled with a third synchronous wheel, the first synchronous wheel, the second synchronous wheel and the third synchronous wheel are all coaxially assembled on or integrally manufactured on the auxiliary shaft where the first synchronous wheel, the second central synchronous wheel and the third central synchronous wheel are all connected with power by adopting synchronous belts; the clutch II is matched with the second central synchronous wheel and is responsible for determining whether the second central synchronous wheel is in force transmission linkage with the relay rod, the clutch III is matched with the third central synchronous wheel and is responsible for determining whether the third central synchronous wheel is in force transmission linkage with the relay rod; the working states of the second clutch and the third clutch at the same moment are consistent, and one of the following three logic relations is needed to be taken and only taken: the second clutch is disconnected and the third clutch is also disconnected at the same time, the second clutch is connected but the third clutch is disconnected at the same time, the second clutch is disconnected but the third clutch is connected at the same time; the first synchronous wheel is driven to operate by the first central synchronous wheel and is driven to operate by a countershaft where the first synchronous wheel is positioned, so that the second synchronous wheel and the third synchronous wheel which are assembled on the countershaft are driven to operate by the countershaft, then the second central synchronous wheel and the third central synchronous wheel are driven to operate respectively by the second synchronous wheel and the third synchronous wheel, when the second clutch is disconnected and the third clutch is also disconnected, the second central synchronous wheel and the third central synchronous wheel are both in transmission relation with the relay rod, when the second clutch is connected and the third clutch is disconnected, the relay rod is driven to operate by the second clutch and the second central synchronous wheel only, and when the second clutch is disconnected and the third clutch is simultaneously connected, the relay rod is driven to operate by the third clutch and the third central synchronous wheel only; the first speed ratio is obtained by the ratio of the number of teeth of the first central synchronous wheel to the number of teeth of the first synchronous wheel, the second speed ratio is obtained by the ratio of the number of teeth of the second synchronous wheel to the number of teeth of the second central synchronous wheel, the third speed ratio is obtained by the ratio of the number of teeth of the third synchronous wheel to the number of teeth of the third central synchronous wheel, the product of the first speed ratio and the second speed ratio is larger than one, and the product of the first speed ratio and the third speed ratio is smaller than one.

Compared with the prior art, the invention has the outstanding advantages that: the axial displacement of the adjusting screw is realized by adopting the tooth difference driving principle and combining a nut screw pair, so that the aim of regulating and controlling the water attack angle of the water pump blade in real time is reliably and accurately realized. On one hand, the structural layout scheme that the adjusting device body and the bearing cover seat are used for jointly positioning and clamping the adjusting nut is adopted, so that the supporting rigidity of a machine part is greatly enhanced, the transmission path of the acting force is shortened, and the capability of the adjusting device for resisting the lifting shaft impact of the water pump is effectively improved; on the other hand, the special adjusting motor of the traditional mechanical adjusting device is thoroughly eliminated, and meanwhile, the structural scheme of the multi-in-one clutch with the central layout is adopted, so that the control system links and the structural layout complexity of the adjusting device are greatly simplified, the manufacturing cost of the device is reduced, the working reliability of the device is improved, the overall height of the device is reduced, the radial size of the device is reduced, and very favorable conditions are created for realizing the compact design of the adjusting device.

Drawings

FIG. 1 is a schematic longitudinal section view of a water pump vane angle in-service adjusting device based on tooth difference driving;

FIG. 2 is a schematic cross-sectional view of the adjustment device of FIG. 1 in the direction K-K;

fig. 3 is a schematic block diagram of the overall layout and installation mechanism of the adjustment device shown in fig. 1.

Detailed Description

The invention is further described below with reference to the specific examples, see fig. 1-3:

the in-service adjusting device for the angle of the water pump blade based on tooth difference driving comprises an adjusting device body 1, an adjusting nut 2 and an adjusting screw 3, wherein the adjusting device body 1 can perform fixed-axis rotary motion around a rotary axis O1 of the adjusting device body, the adjusting nut 2 and the adjusting screw 3 are coaxially arranged with the adjusting device body 1, namely, the axis of the adjusting nut 2 and the axis of the adjusting screw 3 are coincident with the rotary axis O1 of the adjusting device body 1 (but allow deviation or non-coincidence which does not affect the normal operation of the adjusting device and is caused by factors such as manufacturing errors, assembly errors, stress deformation, thermal expansion deformation and the like), the adjusting nut 2 and the adjusting screw 3 are matched in a spiral structure and form a spiral kinematic pair, the adjusting nut 2 can drive the adjusting screw 3 to perform axial displacement motion, wherein the adjusting device body 1 can be arranged on a hollow shaft B of a main motor rotor of the water pump and driven by the adjusting screw, an adjusting pull rod A which is connected with the water pump blade and can change the angle of the blade passes through the hollow shaft B of the main motor rotor of the water pump and then is connected with the adjusting screw 3 of the adjusting device (as shown in 3), when the adjusting nut 2 and the adjusting screw 3 is regulated and the adjusting screw 3 generates axial displacement to perform axial displacement, the adjusting pull rod 3 is pushed out or pushed out of the adjusting screw to regulate the angle to perform axial displacement; the structure of the adjusting device body 1 may be an integral component (not shown in the figure) or an assembly formed by assembling a plurality of parts (as shown in fig. 1), including an assembly formed by welding, riveting, screwing, clamping, bonding, stacking or the like, wherein the assembly is optimally formed by screwing, that is, adopting a screw structure for connection, when the adjusting device body 1 adopts an integral structure, good rigidity is obtained, and when the adjusting device body 1 adopts the structural form of the assembly, flexible design, flexible manufacture and flexible installation of other parts are facilitated; the screw structure of the screw kinematic pair formed by the adjusting nut 2 and the adjusting screw 3 can be various forms in the prior art, including a thread structure, a screw rod structure and the like, wherein the screw kinematic pair formed by the adjusting nut 2 and the adjusting screw 3 has the best self-locking function; it should be noted that the adjusting device of the present invention includes both the blade angle adjusting device for a water pump and the blade angle adjusting device for various water turbines, and also the blade adjusting device in other fluid machines having blades as working units and requiring adjustment of their attack angles; one of the great features of the present invention is that: a bearing cap seat 4 is arranged, the bearing cap 4 is fixedly connected to the adjusting device body 1 (as shown in fig. 1), or the bearing cap 4 and the adjusting device body 1 are integrally manufactured (not shown in the figure), and the bearing cap seat 4 and the adjusting device body 1 together perform synchronous rotary motion around a rotary axis O1; the adjusting nut 2 is provided with an upper bearing surface 5a and a lower bearing surface 5b, the upper bearing surface 5a and the lower bearing surface 5b can be arranged at the shaft ends (not shown in the figure) of the uppermost part and the lowermost part of the adjusting nut 2 or can be arranged on one bearing shaft shoulder 5 (shown in fig. 1) of the adjusting nut 2, wherein the bearing shaft shoulder 5 is fixedly connected on the adjusting nut 2 (not shown in the figure) or the bearing shaft shoulder 5 and the adjusting nut 2 are integrally formed (shown in fig. 1), the lower bearing surface 5b has a mutual bearing relation with the adjusting device body 1, the mutual bearing relation is that a transmission association relation of acting force exists between the upper bearing surface 5a and the bearing cap seat 4, for example, all or part of the downward load force and the gravity applied by the adjusting nut 2 acts on the adjusting device body 1 through the lower bearing surface 5b, the acting mode comprises that the lower bearing surface 5b directly contacts and presses against the adjusting device body 1 (the bearing surface 5b is not shown in the figure) or the sliding bearing surface 1 is not shown in the sliding way, and the sliding device further comprises a thrust bearing surface 1 is not shown in the sliding device 1; the advantage of the present invention is that the positioning and pre-tightening of the adjusting nut 2 can be performed to enhance the overall rigidity of the mating member and the connecting member, on the other hand, the present invention can also effectively resist the impact of the "lifting shaft" (the lifting shaft is the phenomenon that the adjusting pull rod a pushes up in some operation conditions of the water pump blade), the upper bearing surface 5a and the bearing cap 4 have a mutual bearing relationship, which can just support and transfer the forces in the occurrence of the above situations, in addition, the bearing cap 4 can also be used to support other components to play a role of assisting or extending the supporting function of the adjusting device body 1, likewise, the upper bearing surface 5a can directly contact and abut against the bearing cap 4 (at this time, the upper bearing surface 5a and the bearing cap 4 actually form a thrust sliding bearing), and also can make the upper bearing surface 5a indirectly push against the bearing cap 4 through the bearing bush (not shown in the figure) or through the auxiliary thrust bearing 7 (as shown in fig. 1), in particular, when the "lifting shaft" generates the impact force "and the blade generates the impact force can be transferred to the adjusting device body 1 through the adjusting device body 1 and the adjusting device body 1 through the adjusting device body 1, and the impact force can be transferred to the adjusting device body 1 (the adjusting device 1, such as shown in the following: the adjusting nut 2, the bearing shaft shoulder 5, the upper bearing surface 5a, the auxiliary thrust bearing 7, the bearing cover seat 4 and the adjusting device body 1 are all far better than the traditional mechanical adjusting device in impact load force, transmission mode and transmission path during the working condition of lifting the shaft, on one hand, the transmission path is greatly shortened, on the other hand, the acting force is quickly transmitted to the adjusting device body 1, so that the rigidity of relevant parts of the device is greatly improved, and more importantly, the acting force does not influence a speed reducing mechanism of the device any more, and the supporting layout of the pair of core kinematic pairs of the adjusting nut 2 and the adjusting screw 3 is greatly optimized; it is obvious that under the constraint of the adjusting device body 1 and the bearing cover seat 4, the adjusting nut 2 can only rotate around the axis of the adjusting device body and can not move along the axis of the adjusting device body, the adjusting nut 2 can have three running states of forward rotation, reverse rotation and static state relative to the adjusting device body 1, and the three running states respectively correspond to three situations of driving the adjusting screw 3 to move up, down and stop along the direction of the swivel axis O1 (or correspond to three situations of moving down, up and stop), and the specific corresponding situation is determined according to the design requirement of the water pump, in other words, the angle of the adjusting pull rod A of the water pump is respectively in three working states of increasing angle (corresponding to the upward movement of the adjusting screw 3 and the setting requirement of the water pump), decreasing angle (corresponding to the downward movement of the adjusting screw 3 and the setting requirement of the water pump) and locking angle (corresponding to the stopping axial movement of the adjusting screw 3); it should be noted that the upper bearing surface 5a and the lower bearing surface 5b of the present invention may be in the form of a planar structure (as shown in fig. 1), a conical structure (not shown), a spherical structure (not shown), or even other convolute structures (not shown), and the planar structure is the best form thereof; another feature of the present invention is that: a first sun gear 8, a second sun gear 9 and a third sun gear 10 (as shown in fig. 1 and 3) which are coaxially arranged with the adjusting device body 1 are arranged, the first sun gear 8 is matched on the adjusting device body 1 and receives the driving of the adjusting device body 1 (see fig. 1 and 3), or the first sun gear 8 and the adjusting device body 1 are manufactured as a whole (not shown in the figure), and the matching comprises the connection of fastening modes such as various welding, riveting, threaded connection and the like, and also comprises the transmission connection modes such as various key connection, spline connection, pin connection, clamping connection and the like; a relay lever 11 is provided which is arranged coaxially with the adjusting device body 1 and can drive the adjusting nut 2 to operate, the relay lever 11 is connected to the adjusting nut 2 (as shown in fig. 1), or the relay lever 11 and the adjusting nut 2 are integrally formed (not shown in the figure), wherein the relay lever 11 is optimally arranged at the upper region or upper region of the adjusting nut 2 (see fig. 1 and 3), because the optimal arrangement form of the adjusting device is a vertical structure, that is, the optimal arrangement of the rotating axis O1 of the adjusting device body 1 is in a plumb shape (see fig. 1 and 3), at this time, the arrangement of the relay lever 11 at the upper region or upper region of the adjusting nut 2 is beneficial to the transmission arrangement design of the mechanism, it is required that the coaxial arrangement of the relay lever 11 and the adjusting device body 1 in the present invention means that a rotating axis exists, and the rotating axis coincides with the rotating axis O1 of the adjusting device body 1 (a certain deviation is allowed to occur due to fit clearance, fitting error, deformation, expansion deformation, running and the like, but the symmetrical arrangement of the adjusting device can be satisfied even when the adjusting device is not coaxially arranged at the upper region of the adjusting device 2 (see fig. 1 and 3) and the adjusting device is not shown in the normal arrangement of the adjusting device is not shown), wherein the relay rod 11 is of a symmetrical structure and is centrally matched with or integrally manufactured on the adjusting nut 2; the invention is provided with a static seat frame 12 and at least one auxiliary shaft 13 (see fig. 1 to 3), all auxiliary shafts 13 are rotatably arranged on the seat frame 12, each auxiliary shaft 13 is provided with a first gear 14 and a second gear 15 or/and a third gear 16 at the same time, at least one auxiliary shaft 13 is provided with a second gear 15 and at least one auxiliary shaft 13 is provided with a third gear 16, namely, the invention at least comprises a first gear 14, a second gear 15 and a third gear 16, the auxiliary shafts 13 of each auxiliary shaft are simultaneously provided with a first gear 14, a second gear 15 and a third gear 16, the first gear 14, the second gear 15 and the third gear 16 are in optimal condition (as shown in fig. 1 and 3), because the device can obtain better stress conditions, the first gear 14, the second gear 15 and the third gear 16 are coaxially arranged on or integrally manufactured on the auxiliary shaft 13, namely, the first gear 14, the second gear 15 and the third gear 16 are in a common axis of rotation and the second gear 15 are in constant mesh with the first gear 2 and the third gear 16, the rotation of the first gear 1 and the third gear 2 are kept in constant mesh with the sun gear 2, the sun gear 2 is kept in constant mesh with the first gear 2 and the sun gear 16, and the rotation 2 is kept in constant mesh with the rotation 1 and the sun gear 2 is in the constant mesh with the sun gear 2; it should be noted that, the number of the auxiliary shafts 13 in the present invention is preferably two to four (specifically, according to the adjustment force required by the water pump blade), and the auxiliary shafts 13 are preferably in the form of uniform and symmetrical ring cloth, and fig. 1 and 2 show the case of using two auxiliary shafts 13 and symmetrically distributing them; in addition, it should be noted that, the structure of the auxiliary shaft 13 in the present invention may be a solid structure, a hollow structure, or a partially solid structure, and the auxiliary shaft 13 may be provided with various structures, such as various key slots, oil channels, etc., and in particular, the auxiliary shaft 13 may further include a spline structure; the stationary mount 12 means that the mount 12 is stationary with respect to the base C of the main motor of the water pump, the protective cover D of the adjusting device or the ground, but is allowed to be subjected to various excitations during operation of the adjusting device or to various vibrations, jitters and deformations; the seat frame 12 of the invention can be a complete independent component (not shown in the figure) or an assembly formed by a plurality of parts (shown in fig. 1), in particular, the seat frame 12 and the protection cover D can have a fixed connection relationship (see fig. 3), so that the protection cover D can be used for preventing the seat frame 12 from rotating along with the adjusting device body 1 due to the action of friction moment; a second clutch 17 and a third clutch 18 (as shown in fig. 1 and 3) are provided, wherein the second clutch 17 is paired with the second sun gear 9 and the second clutch 17 is responsible for determining whether the second sun gear 9 is in force transmission linkage with the relay lever 11, the third clutch 18 is paired with the third sun gear 10 and the third clutch 18 is responsible for determining whether the third sun gear 10 is in force transmission linkage with the relay lever 11, it is required to say that, since the relay lever 11 in the invention is fastened on the adjusting nut 2 or is made in an integral structure with the adjusting nut 2, the second clutch 17 is paired with the second sun gear 9 and the second clutch 17 is responsible for determining whether the second sun gear 9 is in force transmission linkage with the relay lever 11, the second clutch 17 is responsible for determining whether the second sun gear 9 is in force transmission linkage with the second sun gear 9, the third clutch 18 is likewise in force transmission linkage with the third sun gear 10 is responsible for the third sun gear 10, and the third clutch 10 is also responsible for determining whether the third clutch 10 is in force transmission linkage with the third sun gear 10 is paired with the third sun gear 10 and the third sun gear 10 is responsible for the third sun gear 10; the second clutch 17 and the third clutch 18 are in accordance with the same operating state at the same time and must take one of the following three logical relations: (1) the second clutch 17 is disconnected, and the third clutch 18 is also disconnected, at the same time, the second sun gear 9 and the third sun gear 10 are in a disconnected transmission relation with the relay rod 11, in response to the relay rod 11 not driving the adjusting nut 2, or the adjusting device body 1, the adjusting nut 2, the adjusting screw 3 and the relay rod 11 are in a relatively static state, that is, the blades of the water pump are locked or kept to work at a certain water attack angle; (2) the second clutch 17 is engaged while the third clutch 18 is disengaged, the second sun gear 9 will be in driving motion and power relationship with the relay lever 11 while the third sun gear 10 is in power-uncoupled relationship with the relay lever 11, the power transmission path being: the adjusting device comprises an adjusting device body 1, a first central gear 8, a first gear 14, a countershaft 13, a second gear 15, a second central gear 9 (a second clutch 17), a relay rod 11, an adjusting nut 2, an adjusting screw 3 and an adjusting pull rod A, so that the adjusting screw 3 moves axially along the direction of a rotating axis O1 and drives the adjusting pull rod A to perform corresponding actions; (3) the second clutch 17 is disconnected, and the third clutch 18 is engaged, at this time, the third sun gear 10 will be in a transmission motion and power relationship with the relay lever 11, and the second sun gear 9 is in a power-disconnection relationship with the relay lever 11, and the power transmission path is: the adjusting device comprises an adjusting device body 1, a first central gear 8, a first gear 14, a countershaft 13, a third gear 16, a third central gear 10 (a third clutch 18), a relay rod 11, an adjusting nut 2, an adjusting screw 3 and an adjusting pull rod A, wherein the adjusting screw 3 moves along the direction of a rotating axis O1 in the opposite axial direction to the condition of the front part (2) and drives the adjusting pull rod A to perform corresponding actions; the first gear 14 is driven to operate by the first sun gear 8, the auxiliary shaft 13 where the first gear 14 is positioned is driven to operate by the auxiliary shaft 13, the second gear 15 and the third gear 16 which are assembled on the auxiliary shaft 13 are driven to operate, then the second sun gear 9 and the third sun gear 10 are driven to operate by the second gear 15 and the third gear 16 respectively, when the second clutch 17 is disconnected and the third clutch 18 is also disconnected, the second sun gear 9 and the third sun gear 10 are both in a transmission relation with the relay rod 11, when the second clutch 17 is connected and the third clutch 18 is simultaneously disconnected, the relay rod 11 is driven to operate by the second clutch 17 and the second sun gear 9 only, and when the second clutch 17 is disconnected and the third clutch 18 is simultaneously connected, the relay rod 11 is driven to operate by the third clutch 18 and the third sun gear 10 only; it is not difficult to find that the invention can only adopt a centrally arranged second clutch 17 to enable the second sun gear 9 to simultaneously receive the driving of a plurality of second gears 15 to drive the relay rod 11 to operate, and likewise only adopts a centrally arranged third clutch 18 to enable the third sun gear 10 to simultaneously receive the driving of a plurality of third gears 16 to drive the relay rod 11, namely the invention can realize a multiple-in-one clutch to control the operation state of the adjusting nut 2, thereby greatly omitting the condition that a plurality of clutches (not less than two clutches 17 similar to the invention and not less than two clutches 18 similar to the invention) are necessary to be used in the traditional differential gear driving, and obviously having very important practical significance for reducing the core components of the device and improving the working reliability of the device; in the invention, a first speed ratio is obtained by the ratio of the number of teeth of the first sun gear 8 to the number of teeth of the first gear 14, a second speed ratio is obtained by the ratio of the number of teeth of the second gear 15 to the number of teeth of the second sun gear 9, a third speed ratio is obtained by the ratio of the number of teeth of the third gear 16 to the number of teeth of the third sun gear 10, the product of the first speed ratio and the second speed ratio has a value greater than one, and the product of the first speed ratio and the third speed ratio has a value less than one; under the above circumstances, the moving direction of the adjusting screw 3 in the present invention will depend on the rotating direction of the adjusting device body 1 and the screw direction of the pair of kinematic pairs of the adjusting nut 2 and the adjusting screw 3, and a specific example is: assuming that the adjusting device body 1 is rotated clockwise (when the swivel axis O1 is a plumb arrangement and is viewed from the top view direction), and the screw structure of the adjusting nut 2 and the adjusting screw 3 is in a right-handed configuration, the adjusting screw 2 is in the process of lifting upward when the second clutch 17 is engaged while the third clutch 18 is disengaged, whereas the adjusting screw 2 is in the process of dropping downward when the second clutch 17 is disengaged while the third clutch 18 is engaged; in particular, the second clutch 17 and the third clutch 18 of the present invention may be electromagnetic clutches, magnetic particle clutches, or other existing clutches, wherein the electromagnetic clutch is preferably used, because the control system is simplified. Obviously, the invention adopts the tooth difference driving principle and combines the nut screw pair to realize the axial displacement of the adjusting screw 3, thereby realizing the purpose of regulating the water attack angle of the water pump blade in real time: on one hand, the structural layout scheme that the adjusting device body 1 and the bearing cover seat 4 are used for jointly positioning and clamping the adjusting nut 2 is adopted, so that the supporting rigidity of a machine part is greatly enhanced, the transmission path of the acting force is shortened, and the capability of the adjusting device for resisting the shaft lifting impact of the water pump is effectively improved; on the other hand, the special adjusting motor of the traditional mechanical adjusting device is thoroughly omitted, and a multi-in-one clutch scheme with a central layout is adopted, so that the complexity of the control system links and the structural layout of the adjusting device is greatly simplified, the manufacturing cost of the device is reduced, the working reliability of the device is improved, the overall height of the device is reduced, the radial dimension of the device is reduced, and very favorable conditions are created for realizing the compact design of the adjusting device.

Furthermore, in order to prevent the phenomenon of oil starvation lubrication and even oil starvation lubrication of the kinematic pair of the core component of the adjusting device adjusting nut 2/adjusting screw 3, so as to ensure and improve the working reliability of the adjusting device, the invention can be provided with a special sealing member 19, so as to effectively reduce or even stop the leakage loss and oil slinging loss of the kinematic pair lubricating oil or lubricating grease of the adjusting nut 2/adjusting screw 3, wherein the layout of the sealing member 19 has two forms: one form is that the sealing member 19 moves along with the adjusting screw 3 and is in moving sealing fit with the outer cylindrical surface of the adjusting nut 2 (as shown in fig. 1), and the other form is that the sealing member 19 is coupled to the adjusting nut 2 and is in moving sealing fit with the outer cylindrical surface of the polish rod of the adjusting screw 3 (not shown in the figure); here, the sealing member 19 following the movement of the adjusting screw 3 may have a cylindrical configuration, which may be enclosed around the outer circumference of the adjusting nut 2 and the adjusting screw 3 (see fig. 1), whereby the oil slinging loss may be effectively prevented; it should be noted that the outer cylindrical surface of the adjusting nut 2 in moving sealing engagement with the sealing member 19 may be various cylindrical surfaces, and the best form thereof is a cylindrical surface, because the cylindrical surface has better workability and assemblability, and the sealing is more reliable; in addition, the outer cylindrical surface of the polish rod, which is in motion sealing fit with the sealing member 19, of the adjusting screw 3 may be various cylindrical surfaces, and the best form is a cylindrical surface.

Further, the invention can be provided with a hollow hole channel 20 (see fig. 1) on the relay rod 11, and a displacement signal rod 21 (shown in fig. 1) penetrating through the hole channel 20 of the relay rod 11 is additionally arranged, the displacement signal rod 21 is fastened and connected on the adjusting nut 2, or the displacement signal rod 21 and the adjusting nut 2 are manufactured as an integral structure; the purpose of the displacement signal rod 21 is to transmit the axial displacement information of the adjusting screw 3 from the inside to the outside of the adjusting device, so that the control system can collect the axial displacement information conveniently, respond to the axial displacement information and send out corresponding running instructions.

Further, in order to reduce frictional wear and improve the service life and the working reliability of the related components, a main thrust bearing 6 (shown as 1) may be disposed between the lower bearing surface 5b of the adjusting nut 2 and the adjusting device body 1, so that the adjusting force generated when adjusting the blade angle of the water pump and the gravity of the related components will pass through the water pump adjusting pull rod a→the adjusting screw 3→the adjusting nut 2→ (the bearing shaft shoulder 5→the lower bearing surface 5b→the main thrust bearing 6→the adjusting device body 1, and the purpose of reducing frictional wear may be achieved by means of the main thrust bearing 6. In addition, a secondary thrust bearing 7 (as shown in fig. 1) may be disposed between the upper bearing surface 5a of the adjusting nut 2 and the bearing cap seat 4, and at this time, the pretightening force of the adjusting nut 2 and the upward pushing force generated when the "shaft lifting" impact will be transmitted through the water pump adjusting pull rod a→the adjusting screw 3→the adjusting nut 2→ (the bearing shoulder 5→the upper bearing surface 5a→the secondary thrust bearing 7→the bearing cap seat 4→the adjusting device body 1, so that the transmission path of the impact force can be shortened to be beneficial to resisting the shaft lifting impact, and the friction and wear between the adjusting nut 2 (including the bearing shoulder 5) and the bearing cap seat 4 can be reduced.

Further, in order to facilitate installation and positioning, a radial positioning bearing 22 and an axial supporting bearing 23 (shown in fig. 1) can be arranged between the seat frame 12 and the adjusting device body 1, and the relative position of the seat frame 12 and the adjusting device body 1 can be accurately positioned by means of the radial positioning bearing 22, which has great significance for ensuring the accurate engagement of all gear pairs of the device, and thus the working reliability of the adjusting device can be effectively ensured; in addition, the provision of the axial support bearing 23 makes it possible to support the weight of the individual components of the differential gear drive mechanism on the adjusting device body 1, which is also advantageous for improving the operational reliability of the device. Further, for the convenience of installation and positioning, a lower positioning bearing 24 and an upper positioning bearing 25 may be disposed between the adjusting nut 2 and the adjusting device body 1 (as shown in fig. 1), wherein inner rings of the lower positioning bearing 24 and the upper positioning bearing 25 may be assembled on the adjusting nut 2, outer rings of the lower positioning bearing 24 and the upper positioning bearing 25 may be assembled on the adjusting device body 1 and/or the bearing cap seat 4, and after the lower positioning bearing 24 and the upper positioning bearing 25 are disposed, the adjusting nut 2 may be accurately positioned so that its axis is coaxial with the rotation axis O1 of the adjusting device body 1, which is important for improving the working reliability of the adjusting nut 2 and the adjusting screw 3. Still further, a buffer pad 26 (as shown in fig. 1) or/and a pre-tightening spring (not shown in the figure) may be disposed between the bearing surface 5a of the bearing cap seat 4 and the adjusting nut 2, so as to alleviate and buffer strong shaft-lifting impact force through deformation energy-absorbing effect of the buffer pad 26, so as to protect the adjusting device from damage, where a preferred material for manufacturing the buffer pad 26 is copper; the wave spring is beneficial to adjusting the pretightening force of the bearing cover seat 4 on the main thrust bearing 6, the adjusting nut 2 and the auxiliary thrust bearing 7, so that the fit clearance and the play of the parts can be effectively eliminated, and the bearing cover seat has better fit rigidity and working state.

In order to prevent the occurrence of a sudden power failure during operation of the water pump, which would result in the vanes not falling back to the minimum water attack angle position (the best vane angle of attack is the minimum position before each start of the water pump), an emergency sun gear 27 (as shown in fig. 1-3) and a reset gear 28 (see fig. 2) may be provided, the emergency sun gear 27 being coaxially coupled to the relay rod 11 (as shown in fig. 3) or to the adjustment nut 2 (not shown), the reset gear 28 being in meshing engagement with the emergency sun gear 27 if necessary; it should be noted that, the falling of the blades back to the minimum water attack angle (i.e. the minimum attack angle) is a requirement of the current operation specification of the large water pump unit, because the blades must be adjusted to the minimum water attack angle before the water pump main unit is started so as to reduce the starting load, so as to reduce the impact to the power grid and the impact to the water pump unit; according to the invention, an emergency small motor 29 (see fig. 1) can be adopted, the emergency small motor 29 is used for driving a reset gear 28 through an over-travel clutch (not shown in the figure), then an emergency central gear 27 with a relatively large size is driven by the reset gear 28 with a relatively small size, and finally the relay rod 11 and the adjusting nut 2 are driven by the emergency central gear 27 to move in the falling direction of the adjusting screw 3; in addition, the present invention may also be used to manually drive the reset gear 28 (not shown), i.e. by turning the adjusting screw 3 in the falling direction, and finally return the water pump blade to the minimum water-facing angle position.

In order to further improve the working reliability of the adjusting device, the oil separation cover 30 (see fig. 1) can be assembled on the second clutch 17 and the third clutch 18, the oil separation cover 30 can be arranged to effectively prevent lubricating oil from splashing on the clutches, and the phenomena of slipping and circuit short circuit can be effectively prevented for the case of adopting a dry clutch, so that the working reliability of the clutches is effectively improved, and the final result is that the working reliability of the device is improved.

The invention can make the sum of the numbers of teeth of the first sun gear 8 and the first gear 14 equal to the sum of the numbers of teeth of the second sun gear 9 and the second gear 15 and equal to the sum of the numbers of teeth of the third sun gear 10 and the third gear 16, and the arrangement is considered that the distances from the axes of all auxiliary shafts 13 to the rotary axis O1 are equal, in other words, the axes of the auxiliary shafts 13 can be distributed on the same circumference, so that the gears can adopt the same standard ratio as the standard gears or the gears with the same deflection coefficient and deflection strategy, and the manufacturing process can be greatly simplified. Further, the present invention can make the number of teeth of the second sun gear 9 one less than that of the first sun gear 8 and the number of teeth of the third sun gear 10 one more than that of the first sun gear 8, and the arrangement has the advantage that a speed ratio as large as possible can be obtained with a small number of teeth difference, whereby the overall size of the adjusting device can be made smaller, which is advantageous in realizing a compact design; in this case, the number of teeth of the second gear 15 is one more than the number of teeth of the first gear 14, and the number of teeth of the third gear 16 is one less than the number of teeth of the first gear 14, in other words, the number of teeth differences at this time is two teeth differences.

The invention can make the first gear 14, the second gear 15 and the third gear 16 have the same number of teeth, and the arrangement has the advantages of reducing the specification of the effective gears, simplifying the manufacturing process and reducing the production cost. Further, it is possible to make the number of teeth of the second sun gear 9 one less than that of the first sun gear 8 and the number of teeth of the third sun gear 10 one more than that of the first sun gear 8, and the arrangement is also based on the principle of small teeth difference to achieve a large speed ratio so as to reduce the overall size of the adjusting device to achieve a compact design, in which case the number of teeth difference is one teeth difference and a large reduction ratio can be obtained maximally.

Similarly, the invention can enable the first sun gear 8, the second sun gear 9 and the third sun gear 10 to have the same number of teeth so as to simplify the specification of the gears. In the same way, the invention can also make the number of teeth of the second gear 15 one more than the number of teeth of the first gear 14 and the number of teeth of the third gear 16 one less than the number of teeth of the first gear 14, so that the number of teeth difference is one tooth difference.

Particularly, the in-service adjusting device of the water pump blade angle based on tooth difference driving can be realized by combining a synchronous gear with a synchronous belt (not shown in the figure), and the differential mechanism of the in-service adjusting device adopting the tooth difference driving of the synchronous belt type can be free from lubricating oil, so that the problem of lubricating medium leakage is avoided, the in-service adjusting device is beneficial to maintenance-free use of the device, and the working reliability of the device is further improved; the principle and layout of the device based on synchronous belt driving are similar to those of the device adopting gear driving mode: the adjusting device comprises an adjusting device body 1, an adjusting nut 2 and an adjusting screw 3, wherein the adjusting device body 1 can perform fixed-axis rotary motion around a rotary axis O1 of the adjusting device body, the adjusting nut 2 and the adjusting screw 3 are coaxially arranged with the adjusting device body 1, the adjusting nut 2 and the adjusting screw 3 are matched in a spiral structure and form a spiral kinematic pair, and the adjusting nut 2 can drive the adjusting screw 3 to perform axial displacement motion; the method is characterized in that: a bearing seat 4 is arranged, the bearing seat 4 is fixedly connected to the adjusting device body 1, or the bearing seat 4 and the adjusting device body 1 are manufactured as an integral structure; the adjusting nut 2 is provided with an upper bearing surface 5a and a lower bearing surface 5b, wherein the lower bearing surface 5b has a mutual bearing relation with the adjusting device body 1, the upper bearing surface 5a has a mutual bearing relation with the bearing cover seat 4, the adjusting nut 2 can only rotate around the axis of the adjusting device body 1 and can not move along the axis of the adjusting nut 2 under the mutual constraint of the adjusting device body 1 and the bearing cover seat 4, and the adjusting nut 2 can have three running states of forward rotation, reverse rotation and static state relative to the adjusting device body 1; the device is provided with a first central synchronous wheel, a second central synchronous wheel and a third central synchronous wheel which are coaxially arranged with the adjusting device body 1, wherein the first central synchronous wheel is connected to the adjusting device body 1 in a matching way and receives the driving of the adjusting device body 1, or the first central synchronous wheel and the adjusting device body 1 are manufactured in an integrated structure; the relay rod 11 is coaxially arranged with the adjusting device body 1, the relay rod 11 is matched and connected with the adjusting nut 2, or the relay rod 11 and the adjusting nut 2 are manufactured into an integral structure, and the relay rod 11 can drive the adjusting nut 2 to operate; the auxiliary shafts 13 are all rotatably mounted on the seat frame 12, a first synchronous wheel is assembled on each auxiliary shaft 13, a second synchronous wheel or/and a third synchronous wheel is assembled on each auxiliary shaft 13, at least one auxiliary shaft 13 is assembled with the second synchronous wheel, at least one auxiliary shaft 13 is assembled with the third synchronous wheel, and the first synchronous wheel, the second synchronous wheel and the third synchronous wheel are all coaxially assembled on or integrally manufactured on the auxiliary shaft 13 where the auxiliary shafts are positioned, wherein the first synchronous wheel, the second central synchronous wheel, the third central synchronous wheel and the third central synchronous wheel are all connected with power by adopting synchronous belts in a moving way; a second clutch 17 and a third clutch 18 are arranged, the second clutch 17 is matched with the second central synchronous wheel, the second clutch 17 is responsible for determining whether the second central synchronous wheel is in force transmission linkage with the relay rod 11, the third clutch 18 is matched with the third central synchronous wheel, and the third clutch 18 is responsible for determining whether the third central synchronous wheel is in force transmission linkage with the relay rod 11; the second clutch 17 and the third clutch 18 are in accordance with the same operating state at the same time and must take one of the following three logical relations: the second clutch 17 is disconnected and simultaneously the third clutch 18 is also disconnected, the second clutch 17 is engaged and simultaneously the third clutch 18 is disconnected, the second clutch 17 is disconnected and simultaneously the third clutch 18 is engaged; the first synchronous wheel is driven to operate by the first central synchronous wheel, the auxiliary shaft 13 where the first synchronous wheel is positioned is driven to operate by the auxiliary shaft 13, the second synchronous wheel and the third synchronous wheel which are assembled on the auxiliary shaft 13 are driven to operate by the auxiliary shaft 13, the second central synchronous wheel and the third central synchronous wheel are driven to operate respectively by the second synchronous wheel and the third synchronous wheel, when the second clutch 17 is disconnected and the third clutch 18 is also disconnected, the second central synchronous wheel and the third central synchronous wheel are both in a transmission relation with the relay rod 11, when the second clutch 17 is connected and the third clutch 18 is simultaneously disconnected, the relay rod 11 is driven to operate by the second clutch 17 and the second central synchronous wheel only, and when the second clutch 17 is disconnected and the third clutch 18 is simultaneously connected, the relay rod 11 is driven to operate by the third clutch 18 and the third central synchronous wheel only; the first speed ratio is obtained by the ratio of the number of teeth of the first central synchronous wheel to the number of teeth of the first synchronous wheel, the second speed ratio is obtained by the ratio of the number of teeth of the second synchronous wheel to the number of teeth of the second central synchronous wheel, the third speed ratio is obtained by the ratio of the number of teeth of the third synchronous wheel to the number of teeth of the third central synchronous wheel, the product of the first speed ratio and the second speed ratio is larger than one, and the product of the first speed ratio and the third speed ratio is smaller than one.

Compared with the prior art, the invention has the outstanding advantages that: the axial displacement of the adjusting screw 3 is realized by adopting the tooth difference driving principle and combining a nut screw pair, so that the aim of regulating and controlling the water attack angle of the water pump blade in service in real time is reliably and accurately realized. On one hand, the structural layout scheme that the adjusting device body 1 and the bearing cover seat 4 are used for jointly positioning and clamping the adjusting nut 2 is adopted, so that the supporting rigidity of a machine part is greatly enhanced, the transmission path of the acting force is shortened, and the capability of the adjusting device for resisting the shaft lifting impact of the water pump is effectively improved; on the other hand, the special adjusting motor of the traditional mechanical adjusting device is thoroughly omitted, and a multi-in-one type central layout clutch structure layout scheme is adopted, so that the control system links and the structural layout complexity of the adjusting device are greatly simplified, the manufacturing cost of the device is reduced, the working reliability of the device is improved, the overall height of the device is reduced, the radial size of the device is reduced, and very favorable conditions are created for realizing compact design of the adjusting device.

The above embodiment is only one of the preferred embodiments of the present invention, and is not intended to limit the scope of the present invention. All equivalent changes according to the structure, shape and principle of the present invention should be covered in the protection scope of the present invention.

Claims

1. The in-service water pump blade angle adjusting device based on tooth difference driving comprises an adjusting device body, an adjusting nut and an adjusting screw, wherein the adjusting device body can perform fixed-axis rotary motion around a rotary axis of the adjusting device body, the adjusting nut and the adjusting screw are coaxially arranged with the adjusting device body, the adjusting nut and the adjusting screw are matched in a spiral structure and form a spiral kinematic pair, and the adjusting nut can drive the adjusting screw to perform axial displacement motion; the method is characterized in that: the bearing cover seat is fixedly connected to the adjusting device body or is manufactured in an integrated structure with the adjusting device body; the adjusting nut is provided with an upper bearing surface and a lower bearing surface, wherein the lower bearing surface and the adjusting device body are in mutual bearing relation, the upper bearing surface and the bearing cover seat are in mutual bearing relation, the adjusting nut can only rotate around the axis of the adjusting device body and can not move along the axis of the adjusting nut under the joint constraint of the adjusting device body and the bearing cover seat, and the adjusting nut can have three running states of forward rotation, reverse rotation and static state relative to the adjusting device body; the device comprises a first central gear, a second central gear and a third central gear which are coaxially arranged with the adjusting device body, wherein the first central gear is connected to the adjusting device body in a matching way and receives the driving of the adjusting device body, or the first central gear and the adjusting device body are manufactured in an integrated structure; the relay rod is coaxially arranged with the adjusting device body, is matched with the adjusting nut or is manufactured in an integrated structure with the adjusting nut, and can drive the adjusting nut to operate; the auxiliary shafts are all rotatably mounted on the seat frame, each auxiliary shaft is provided with a first gear, at least one of a second gear and a third gear, at least one auxiliary shaft is provided with a second gear, at least one auxiliary shaft is provided with a third gear, the first gear, the second gear and the third gear are all coaxially connected to or integrally manufactured on the auxiliary shaft, and the first gear and the first central gear are kept in constant mesh, the second gear and the second central gear are kept in constant mesh, and the third gear and the third central gear are kept in constant mesh; the clutch II is matched with the second central gear and is responsible for determining whether the second central gear is in force transmission linkage with the relay rod, the clutch III is matched with the third central gear and is responsible for determining whether the third central gear is in force transmission linkage with the relay rod; the working states of the second clutch and the third clutch at the same moment are consistent, and one of the following three logic relations can be taken only: the second clutch is disconnected and the third clutch is also disconnected at the same time, the second clutch is connected but the third clutch is disconnected at the same time, the second clutch is disconnected but the third clutch is connected at the same time; the first gear is driven to operate by the first central gear and is driven to operate by a countershaft where the first gear is positioned, so that the countershaft drives a second gear and a third gear which are assembled on the countershaft to operate, then the second central gear and the third central gear are driven to operate respectively by the second gear and the third gear, when the second clutch is disconnected and the third clutch is also disconnected, the second central gear and the third central gear are both disconnected from a relay lever, when the second clutch is connected and the third clutch is disconnected, the relay lever is driven to operate only by the second clutch and the second central gear, and when the second clutch is disconnected and the third clutch is connected, the relay lever is driven to operate only by the third clutch and the third central gear; the first speed ratio is obtained by the ratio of the number of teeth of the first sun gear to the number of teeth of the first sun gear, the second speed ratio is obtained by the ratio of the number of teeth of the second sun gear to the number of teeth of the second sun gear, and the third speed ratio is obtained by the ratio of the number of teeth of the third sun gear, the product of the first speed ratio and the second speed ratio has a value greater than one, and the product of the first speed ratio and the third speed ratio has a value less than one.

2. The tooth difference driving-based water pump blade angle in-service adjusting device according to claim 1, wherein the tooth difference driving-based water pump blade angle in-service adjusting device is characterized in that: a sealing member is arranged, and the sealing member moves along with the adjusting screw rod and is in sealing fit with the outer cylindrical surface of the adjusting nut, or the sealing member is matched on the adjusting nut and is in sealing fit with the outer cylindrical surface of the polished rod of the adjusting screw rod.

3. The tooth difference driving-based water pump blade angle in-service adjusting device according to claim 2, wherein: the relay rod is provided with a hollow pore canal, and is additionally provided with a displacement signal rod which penetrates through the pore canal of the relay rod, and the displacement signal rod is fixedly connected to the adjusting nut or is manufactured in an integrated structure with the adjusting nut.

4. The tooth difference driving-based water pump blade angle in-service adjusting device according to claim 3, wherein: and a main thrust bearing is arranged between the lower bearing surface of the bearing shaft shoulder of the adjusting nut and the adjusting device body.

5. The tooth difference drive-based water pump blade angle in-service adjusting device according to claim 4, wherein: a radial positioning bearing and an axial supporting bearing are arranged between the seat frame and the adjusting device body.

6. The tooth difference drive-based water pump blade angle in-service adjusting device according to claim 5, wherein: a lower positioning bearing and an upper positioning bearing are arranged between the adjusting nut and the adjusting device body.

7. The tooth difference drive-based water pump blade angle in-service adjusting device according to claim 6, wherein: and a buffer gasket or/and a pre-tightening spring are arranged between the bearing cover seat and the bearing surface on the adjusting nut.

8. The tooth difference drive-based water pump vane angle in-service adjusting device according to any one of claims 1 to 7, wherein: an emergency sun gear and a reset gear are arranged, the emergency sun gear is coaxially matched on the relay rod or the adjusting nut, and the reset gear can be meshed and matched with the emergency sun gear.

9. The tooth difference drive-based water pump vane angle in-service adjusting device according to any one of claims 1 to 7, wherein: the second clutch and the third clutch are both provided with an oil separation cover.

10. The tooth difference drive-based water pump vane angle in-service adjusting device according to any one of claims 1 to 7, wherein: the sum of the numbers of teeth of the first sun gear and the first gear is equal to the sum of the numbers of teeth of the second sun gear and the second gear and is equal to the sum of the numbers of teeth of the third sun gear and the third gear.

11. The tooth difference drive-based water pump blade angle in-service adjusting device according to claim 10, wherein: the number of teeth of the second sun gear is one less than the number of teeth of the first sun gear, and the number of teeth of the third sun gear is one more than the number of teeth of the first sun gear.

12. The tooth difference drive-based water pump vane angle in-service adjusting device according to any one of claims 1 to 7, wherein: the first gear, the second gear and the third gear have the same number of teeth.

13. The tooth difference drive-based water pump blade angle in-service adjusting device according to claim 12, wherein: the number of teeth of the second sun gear is one less than the number of teeth of the first sun gear, and the number of teeth of the third sun gear is one more than the number of teeth of the first sun gear.

14. The tooth difference drive-based water pump vane angle in-service adjusting device according to any one of claims 1 to 7, wherein: the first sun gear, the second sun gear and the third sun gear have the same number of teeth.

15. The tooth difference drive-based water pump blade angle in-service adjusting device according to claim 14, wherein: the number of teeth of the second gear is one more than that of the first gear, and the number of teeth of the third gear is one less than that of the first gear.

16. The in-service water pump blade angle adjusting device based on tooth difference driving comprises an adjusting device body, an adjusting nut and an adjusting screw, wherein the adjusting device body can perform fixed-axis rotary motion around a rotary axis of the adjusting device body, the adjusting nut and the adjusting screw are coaxially arranged with the adjusting device body, the adjusting nut and the adjusting screw are matched in a spiral structure and form a spiral kinematic pair, and the adjusting nut can drive the adjusting screw to perform axial displacement motion; the method is characterized in that: the bearing cover seat is fixedly connected to the adjusting device body or is manufactured in an integrated structure with the adjusting device body; the adjusting nut is provided with an upper bearing surface and a lower bearing surface, wherein the lower bearing surface and the adjusting device body are in mutual bearing relation, the upper bearing surface and the bearing cover seat are in mutual bearing relation, the adjusting nut can only rotate around the axis of the adjusting device body and can not move along the axis of the adjusting nut under the joint constraint of the adjusting device body and the bearing cover seat, and the adjusting nut can have three running states of forward rotation, reverse rotation and static state relative to the adjusting device body; the device comprises a regulating device body, a first central synchronous wheel, a second central synchronous wheel and a third central synchronous wheel, wherein the first central synchronous wheel, the second central synchronous wheel and the third central synchronous wheel are coaxially arranged with the regulating device body, and the first central synchronous wheel is connected to the regulating device body in a matched mode and receives the driving of the regulating device body, or the first central synchronous wheel and the regulating device body are manufactured in an integrated structure; the relay rod is coaxially arranged with the adjusting device body, is matched with the adjusting nut or is manufactured in an integrated structure with the adjusting nut, and can drive the adjusting nut to operate; the device comprises a static seat frame and at least one auxiliary shaft, wherein the auxiliary shafts are all rotatably arranged on the seat frame, each auxiliary shaft is provided with a first synchronous wheel, a second synchronous wheel and at least one of a third synchronous wheel, at least one auxiliary shaft is provided with the second synchronous wheel, at least one auxiliary shaft is provided with the third synchronous wheel, the first synchronous wheel, the second synchronous wheel and the third synchronous wheel are all coaxially connected with or integrally manufactured on the auxiliary shaft where the auxiliary shaft is positioned, and the first synchronous wheel, the second central synchronous wheel, the third synchronous wheel and the third central synchronous wheel are all connected with power by adopting synchronous belts in a moving way; the clutch II is matched with the second central synchronous wheel and is responsible for determining whether the second central synchronous wheel is in force transmission linkage with the relay rod, the clutch III is matched with the third central synchronous wheel and is responsible for determining whether the third central synchronous wheel is in force transmission linkage with the relay rod; the working states of the second clutch and the third clutch at the same moment are consistent, and one of the following three logic relations can be taken only: the second clutch is disconnected and the third clutch is also disconnected at the same time, the second clutch is connected but the third clutch is disconnected at the same time, the second clutch is disconnected but the third clutch is connected at the same time; the first synchronous wheel is driven to operate by the first central synchronous wheel and is driven to operate by a countershaft where the first synchronous wheel is positioned, so that the second synchronous wheel and the third synchronous wheel which are assembled on the countershaft are driven to operate by the countershaft, then the second central synchronous wheel and the third central synchronous wheel are driven to operate respectively by the second synchronous wheel and the third synchronous wheel, when the second clutch is disconnected and the third clutch is also disconnected, the second central synchronous wheel and the third central synchronous wheel are both in transmission relation with the relay rod, when the second clutch is connected and the third clutch is disconnected, the relay rod is driven to operate by the second clutch and the second central synchronous wheel only, and when the second clutch is disconnected and the third clutch is simultaneously connected, the relay rod is driven to operate by the third clutch and the third central synchronous wheel only; the first speed ratio is obtained by the ratio of the number of teeth of the first central synchronous wheel to the number of teeth of the first synchronous wheel, the second speed ratio is obtained by the ratio of the number of teeth of the second synchronous wheel to the number of teeth of the second central synchronous wheel, the third speed ratio is obtained by the ratio of the number of teeth of the third synchronous wheel to the number of teeth of the third central synchronous wheel, the product of the first speed ratio and the second speed ratio is larger than one, and the product of the first speed ratio and the third speed ratio is smaller than one.