阅读说明：本技术 分体式叶片、流体驱动装置以及流体驱动比例混合器 (Split blade, fluid driving device and fluid driven proportional mixer ) 是由 不公告发明人 于 2020-09-18 设计创作，主要内容包括：一种分体式叶片、流体驱动装置以及流体驱动比例混合器。该分体式叶片,用于作为流体驱动装置的配件以将流体的压力能转化成机械能。该分体式叶片包括：一或多个顶杆,其中每该顶杆适于被可径向滑动地设置于该流体驱动装置的转子；和二阀片,其中两个该阀片分别被平行地安装于该顶杆的两端部,并且每该阀片沿着该顶杆向外延伸,以形成具有贯穿顶杆式结构的该分体式叶片；凭此,当该分体式叶片在该流体的作用下带动该转子旋转时,每该分体式叶片的该顶杆相对于该转子进行径向滑动,以使每该阀片的外边部能够始终接触该流体驱动装置的定子的内壁,有助于减少该液体驱动装置的漏液。(A split blade, a fluid driving device and a fluid driven proportioner. The split blade is used as a fitting of a fluid driving device to convert pressure energy of a fluid into mechanical energy. This split type blade includes: one or more rams, wherein each ram is adapted to be radially slidably disposed on a rotor of the fluid drive device; two valve plates are respectively arranged at two ends of the ejector rod in parallel, and each valve plate extends outwards along the ejector rod to form the split type blade with a penetrating ejector rod type structure; therefore, when the split type blades drive the rotor to rotate under the action of the fluid, the ejector rods of each split type blade slide radially relative to the rotor, so that the outer edge of each valve plate can always contact with the inner wall of the stator of the fluid driving device, and the leakage of the fluid driving device is reduced.)

1. A split blade for use as a fitting to a fluid driven device for converting pressure energy of a fluid into mechanical energy, wherein the split blade comprises:

one or more rams, wherein each said ram is adapted to be radially slidably disposed to a rotor of the fluid drive device; and

the two valve plates are respectively arranged at two end parts of the ejector rod in parallel, and each valve plate extends outwards along the ejector rod to form the split type blade with a penetrating ejector rod type structure; therefore, when the split type blades drive the rotor to rotate under the action of the fluid, the ejector rods of each split type blade slide radially relative to the rotor, so that the outer edge of each valve plate can always contact with the inner wall of the stator of the fluid driving device.

2. The split blade of claim 1, wherein the lift pin and the valve plate are made of different materials, and the strength of the material of the lift pin is greater than that of the material of the valve plate.

3. The split blade of claim 2, wherein the carrier rod is made of a metal material and the valve plate is made of a non-metal material.

4. The split blade of claim 1, wherein a plurality of the lift pins are uniformly spaced, and both the end portions of each of the lift pins are connected to the inner side portions of both the valve sheets, respectively.

5. The split vane of claim 4, wherein the inner edge of the valve plate is provided with one or more fitting grooves, and the end of the lift pin is inserted into the fitting groove of the valve plate to rigidly or flexibly connect the lift pin to the valve plate.

6. The split blade of claim 5, further comprising one or more reinforcing members, wherein the reinforcing members are correspondingly disposed at the connecting portions of the valve plate and the lift pins to reinforce the connecting strength of the valve plate and the lift pins.

7. The split blade of claim 6, wherein the reinforcing member is a pair of reinforcing ribs symmetrically disposed at front and rear sides of the fitting groove of the valve sheet, and each of the reinforcing ribs extends from the inner edge portion of the valve sheet to the outer edge portion of the valve sheet.

8. The split blade of claim 6, wherein the reinforcing member is a reinforcing rib provided at a rear side of the fitting groove of the valve sheet, respectively, and the reinforcing rib extends from the inner edge portion of the valve sheet to the outer edge portion of the valve sheet.

9. The split vane of claim 8, wherein the fitting groove of the valve plate is eccentrically provided rearward to the inner edge portion of the valve plate so as to be located at a junction of the inner edge portion of the valve plate and the reinforcing rib.

10. The split blade of claim 9, wherein a cross-sectional area of a middle portion of the lift pin is larger than a cross-sectional area of the end portions of the lift pin, and the two end portions of the lift pin integrally extend outward from opposite ends of the middle portion of the lift pin in a direction parallel to a center line of the middle portion, respectively.

11. The split vane of any one of claims 1 to 10, wherein the outer edge portion of the valve plate has an arcuate end surface, and the arcuate end surface has a double radius of curvature arcuate configuration or a single radius of curvature arcuate configuration.

12. The split vane of claim 11, wherein the arc end surface having the double curvature radius arc structure has an arc portion having a larger curvature radius having the same curvature radius as an envelope of the inner wall of the stator at a negative displacement region.

13. The split vane of any one of claims 1 to 10, further comprising at least two elastic members, wherein each elastic member is correspondingly disposed on a middle end surface of the outer edge portion of the valve plate, and is used for being located between the valve plate and the stator to perform a sealing function when the valve plate is located in a positive displacement region or a negative displacement region of the stator.

14. The split blade of any one of claims 1 to 10, wherein the ejector rod is flexibly connected with the valve plate through a fastener or a micro spring; or the ejector rod is rigidly connected with the valve plate through interference fit.

15. A fluid driving device for partially converting pressure energy of a fluid into mechanical energy, wherein the fluid driving device comprises:

at least one stator, wherein each stator has an inner cavity;

at least one rotor, wherein each said rotor is rotatably disposed within said interior cavity of a respective said stator; and

at least two split blades, wherein each split blade is radially slidably mounted to a respective rotor, and each split blade comprises:

one or more rams, wherein each ram is adapted to be radially slidably disposed to the rotor; and

the two valve plates are respectively arranged at two end parts of the ejector rod in parallel, and each valve plate extends outwards along the ejector rod to form the split type blade with a penetrating ejector rod type structure; therefore, when the split blades drive the rotor to rotate under the action of the fluid, the ejector rod of each split blade slides radially relative to the rotor, so that the outer edge of each valve plate can always contact with the inner wall of the stator.

16. A fluid driving device as claimed in claim 15 wherein said rotor has at least two through holes, wherein each said through hole extends in a radial direction of said rotor to extend through said rotor for slidably mounting said split blades.

17. The fluid driving device as claimed in claim 16, wherein each of the through holes of the rotor includes one or more sliding holes and two telescopic slots, wherein two of the telescopic slots are symmetrically located at the outer circumference of the rotor, and the sliding holes communicatively extend from one telescopic slot to the other telescopic slot, wherein the plunger of the split vane is slidably mounted to the sliding hole of the rotor, and the valve plate is telescopically mounted to the telescopic slot of the rotor.

18. The fluid driving device as claimed in claim 17, wherein the rotor further has at least two pairs of seal grooves, wherein each pair of seal grooves is respectively and correspondingly disposed on sidewalls of two telescopic grooves of the through hole of the rotor for receiving a seal to seal a gap between the valve plate and the rotor by the seal.

19. The fluid driving device as claimed in claim 18, wherein the split vane further comprises one or more reinforcing members, wherein the reinforcing members are correspondingly disposed at the connecting portions of the valve plate and the lift pins to reinforce the connecting strength of the valve plate and the lift pins; wherein the rotor further has an eccentric groove extending rearward from the telescopic slot or concentric grooves extending forward and rearward from the telescopic slot simultaneously for slidably receiving the reinforcing member.

20. A fluid driving device according to any one of claims 15 to 19 wherein the rotor is further provided with a plurality of balance holes, wherein each balance hole is located on the rotor and communicates with the bottom of a corresponding telescopic slot, and when the vane of the split vane slides to the inlet and outlet regions of the stator, the balance holes are used to introduce the fluid into the corresponding telescopic slot to balance the pressure difference across the vane.

21. A fluid driven proportioner for proportioned mixing of a first fluid and a second fluid, wherein the fluid driven proportioner comprises:

a fluid driving device for partially converting pressure energy of the first fluid flowing into the fluid driving device into mechanical energy and outputting the first fluid, wherein the fluid driving device comprises:

at least one stator, wherein each stator has an inner cavity;

at least one rotor, wherein each said rotor is rotatably disposed within said interior cavity of a respective said stator; and

at least two split blades, wherein each split blade is radially slidably mounted to a respective rotor, and each split blade comprises:

one or more rams, wherein each ram is adapted to be radially slidably disposed to the rotor; and

the two valve plates are respectively arranged at two end parts of the ejector rod in parallel, and each valve plate extends outwards along the ejector rod to form the split type blade with a penetrating ejector rod type structure; therefore, when the split blades drive the rotor to rotate under the action of the fluid, the ejector rod of each split blade slides radially relative to the rotor, so that the outer edge of each valve plate can always contact with the inner wall of the stator.

A pump device for converting mechanical energy into pressure energy of the second fluid during operation and outputting the second fluid; and

a coupling, wherein the coupling couples the fluid driving device to the pump device for transferring the mechanical energy converted by the fluid driving device to the pump device to drive the pump device to operate, so that the first fluid output by the fluid driving device can be mixed with the second fluid output by the pump device according to a predetermined ratio.

Technical Field

The invention relates to the technical field of fluid driving, in particular to a split blade, a fluid driving device and a fluid driven proportional mixer.

Background

Fluid driving devices such as hydraulic motors have been widely used in various fields such as industry, agriculture, and fire fighting as an energy conversion device for converting pressure energy of a fluid into mechanical energy. The present market shows that a hydraulic motor generally comprises a housing, a stator, a rotor and a blade, wherein the stator is fixedly arranged in the housing, the blade is radially slidably arranged in the rotor, but the rotor is eccentrically arranged in an inner cavity of the stator, and when the blade drives the rotor to rotate under the action of fire-fighting water, the blade slides along the radial direction of the rotor, so that the end surface of the blade directly contacts the inner cavity wall surface of the stator.

Existing hydraulic motors typically employ conventional blades that are radially slidably inserted at one end into the rotor such that the other end of the conventional blade is thrown out under centrifugal force to contact the inner cavity wall of the stator. However, such conventional vanes are generally suitable for hydraulic motors with higher rotation speed, because at low rotation speed, the conventional vanes cannot be thrown out due to too small centrifugal force, so that a larger gap exists between the conventional vanes and the stator, which causes serious leakage and even influences the normal operation of the hydraulic motor.

In order to solve the above problems, some existing hydraulic motors are additionally provided with a spring structure, so that the conventional vane can be ejected to contact the inner cavity wall of the stator by using a spring force at a low rotation speed. However, since the spring structure has a large stroke and generates a large spring compression force, the force between the conventional vane and the stator is also large, which causes severe abrasion between the conventional vane and the stator and generates a large noise, which greatly shortens the service life of the hydraulic motor.

In addition, some hydraulic motors do not directly give up with the conventional vane, but adopt an integral penetrating vane with a one-piece structure, that is, the integral penetrating vane is penetratively disposed on the rotor, and the integral penetrating vane can slide along the radial direction of the rotor, so that both end portions of the integral penetrating vane can always contact the inner cavity wall of the stator at any rotation speed to valve on the inner cavity wall of the stator. However, since the integrated penetrating blade is a single piece, it is difficult to have high flatness, and the integrated penetrating blade slidably penetrates the rotor, a large gap must exist between the integrated penetrating blade and the rotor, and wear is severe due to a large contact area between the integrated penetrating blade and the rotor, which still has a problem of serious liquid leakage.

Disclosure of Invention

An object of the present invention is to provide a split blade, a fluid driving device, and a fluid driven proportioner, which can reduce the clearance between the blade and the rotor, and contribute to reducing the leakage of the fluid driving device.

Another object of the present invention is to provide a split blade, a fluid driving device and a fluid driven proportioner, wherein, in an embodiment of the present invention, the split blade employs a through ejector structure to reduce the contact area and the gap between the split blade and the rotor while ensuring the low-speed operation of the fluid driving device, which helps to reduce the wear and the leakage.

It is another object of the present invention to provide a split vane, a fluid driven device and a fluid driven proportioner, wherein the split vane can have a high flatness, which helps to reduce the wear and noise generated during the operation of the fluid driven device.

Another object of the present invention is to provide a split vane, a fluid driving device and a fluid driven proportioner, wherein in an embodiment of the present invention, the top rod of the split vane can be made of a metal material to have a high precision, which helps to further reduce the gap between the split vane and the rotor to reduce liquid leakage as much as possible.

Another object of the present invention is to provide a split vane, a fluid driving device and a fluid driven proportioner, wherein, in an embodiment of the present invention, the valve plate of the split vane can be made of plastic, which helps to reduce the overall weight of the split vane, reduce the wear of the split vane and the stator, and reduce the noise during operation.

Another object of the present invention is to provide a split vane, a fluid driving device and a fluid driven proportioner, wherein, in an embodiment of the present invention, the valve plate of the split vane is provided with a rib, which helps to enhance the strength of the valve plate to prevent the valve plate from being deformed and damaged.

Another object of the present invention is to provide a split vane, a fluid driving device and a fluid driven proportioner, wherein, in an embodiment of the present invention, the reinforcing rib of the split vane is located at the connection position of the valve plate and the ejector rod, which helps to improve the connection strength and connection stability of the valve plate and the ejector rod.

Another object of the present invention is to provide a split vane, a fluid driving device and a fluid driven proportioner, wherein, in an embodiment of the present invention, the top of the valve plate of the split vane has a circular arc structure with double curvature radius, which helps to reduce leakage and abrasion between the valve plate and the stator.

Another object of the present invention is to provide a split vane, a fluid driving device and a fluid driven proportioner, wherein, in an embodiment of the present invention, the fluid driving device can balance the radial pressure difference of the valve plate of the split vane by using a balance hole provided on a rotor, so as to reduce the abrasion between the split vane and the rotor.

It is another object of the present invention to provide a split vane, fluid driven device and fluid driven proportioner wherein the use of expensive materials or complex structures is not required in order to achieve the above objects. The present invention therefore successfully and effectively provides a solution that not only provides a simple split blade, fluid drive and fluid driven proportioner, but also increases the utility and reliability of the split blade, fluid drive and fluid driven proportioner.

To achieve at least one of the above objects and other objects and advantages, the present invention provides a split blade for use as a fitting of a fluid driving device to convert pressure energy of a fluid into mechanical energy, wherein the split blade comprises:

one or more rams, wherein each said ram is adapted to be radially slidably disposed to a rotor of the fluid drive device; and

the two valve plates are respectively arranged at two end parts of the ejector rod in parallel, and each valve plate extends outwards along the ejector rod to form the split type blade with a penetrating ejector rod type structure; therefore, when the split type blades drive the rotor to rotate under the action of the fluid, the ejector rods of each split type blade slide radially relative to the rotor, so that the outer edge of each valve plate can always contact with the inner wall of the stator of the fluid driving device.

In an embodiment of the invention, the ejector rod and the valve plate are made of different materials, and the material strength of the ejector rod is greater than that of the valve plate.

In an embodiment of the invention, the ejector rod is made of a metal material, and the valve plate is made of a non-metal material.

In an embodiment of the present invention, the plurality of lift pins are uniformly spaced, and two end portions of each of the lift pins are respectively connected to inner side portions of the two valve plates.

In an embodiment of the invention, one or more fitting grooves are formed on the inner edge of the valve plate, wherein the end of the lift pin is inserted into the fitting groove of the valve plate to rigidly or flexibly connect the lift pin with the valve plate.

In an embodiment of the invention, the split vane further includes one or more reinforcing elements, wherein the reinforcing elements are correspondingly disposed on the valve plate at a position connected to the ejector rod to reinforce the connection strength between the valve plate and the ejector rod.

In an embodiment of the invention, the reinforcing element is a pair of reinforcing ribs symmetrically disposed at front and rear sides of the fitting groove of the valve plate, and each of the reinforcing ribs extends from the inner edge portion of the valve plate to the outer edge portion of the valve plate.

In an embodiment of the invention, the reinforcing element is a reinforcing rib correspondingly disposed at front and rear sides of the fitting groove of the valve plate, and the reinforcing rib extends from the inner edge portion of the valve plate to the outer edge portion of the valve plate.

In an embodiment of the present invention, the fitting groove of the valve plate is eccentrically disposed rearward at the inner side portion of the valve plate, so that the fitting groove is located at a connection of the inner side portion of the valve plate and the reinforcing rib.

In an embodiment of the present invention, a cross-sectional area of a middle portion of the jack is larger than a cross-sectional area of the end portion of the jack, and both the end portions of the jack integrally extend outward from opposite ends of the middle portion of the jack in a direction parallel to a center line of the middle portion, respectively.

In an embodiment of the present invention, the outer edge portion of the valve plate has an arc-shaped end surface, and the arc-shaped end surface has a double curvature radius arc structure or a single curvature radius arc structure.

In an embodiment of the present invention, the arc portion with a larger curvature radius on the arc end surface having the double curvature radius arc structure has the same curvature radius as an envelope curve of the inner wall of the stator at the negative displacement region.

In an embodiment of the invention, the split vane further includes at least two elastic members, where each elastic member is correspondingly disposed on a middle end surface of the outer edge portion of the valve plate, and is used for positioning the elastic member between the valve plate and the stator to perform a sealing function when the valve plate is in a positive displacement region or a negative displacement region of the stator.

In one embodiment of the invention, the ejector rod is flexibly connected with the valve plate through a fastener or a miniature spring; or the ejector rod is rigidly connected with the valve plate through interference fit.

According to another aspect of the present invention, there is further provided a fluid driving device for converting pressure energy of a fluid into mechanical energy, wherein the fluid driving device comprises:

at least one stator, wherein each stator has an inner cavity;

at least one rotor, wherein each said rotor is rotatably disposed within said interior cavity of a respective said stator; and

at least two split blades, wherein each split blade is radially slidably mounted to a respective rotor, and each split blade comprises:

one or more rams, wherein each ram is adapted to be radially slidably disposed to the rotor; and

the two valve plates are respectively arranged at two end parts of the ejector rod in parallel, and each valve plate extends outwards along the ejector rod to form the split type blade with a penetrating ejector rod type structure; therefore, when the split blades drive the rotor to rotate under the action of the fluid, the ejector rod of each split blade slides radially relative to the rotor, so that the outer edge of each valve plate can always contact with the inner wall of the stator.

In an embodiment of the present invention, the rotor has at least two through holes, wherein each through hole extends along a radial direction of the rotor to penetrate the rotor for slidably mounting the split blades.

In an embodiment of the present invention, each of the through holes of the rotor includes one or more sliding holes and two telescopic slots, wherein two of the telescopic slots are symmetrically located at the outer circumference of the rotor, and the sliding holes communicatively extend from one of the telescopic slots to the other telescopic slot, wherein the plunger of the split vane is slidably mounted to the sliding hole of the rotor, and the valve plate is telescopically mounted to the telescopic slot of the rotor.

In an embodiment of the invention, the rotor further has at least two pairs of sealing grooves, wherein each pair of sealing grooves is correspondingly disposed on sidewalls of two telescopic grooves of the through hole of the rotor, respectively, for accommodating a sealing member, so as to seal a gap between the valve plate and the rotor by the sealing member.

In an embodiment of the invention, the split blade further includes one or more reinforcing elements, wherein the reinforcing elements are correspondingly disposed on the valve plate at a position connected with the ejector rod to reinforce the connection strength of the valve plate and the ejector rod; wherein the rotor further has an eccentric groove extending rearward from the telescopic slot or concentric grooves extending forward and rearward from the telescopic slot simultaneously for slidably receiving the reinforcing member.

In an embodiment of the present invention, the rotor is further provided with a plurality of balancing holes, wherein each balancing hole is located on the rotor and is communicated with the bottom of the corresponding telescopic slot, and when the valve plate of the split vane slides to the inlet area and the outlet area of the stator, the balancing hole corresponding to the valve plate is used for introducing the fluid into the telescopic slot to balance the radial pressure difference of the valve plate.

According to another aspect of the present invention, there is further provided a fluid driven proportioner for proportioning a first fluid and a second fluid, wherein the fluid driven proportioner comprises:

a fluid driving device for partially converting pressure energy of the first fluid flowing into the fluid driving device into mechanical energy and outputting the first fluid, wherein the fluid driving device comprises:

at least one stator, wherein each stator has an inner cavity;

at least one rotor, wherein each said rotor is rotatably disposed within said interior cavity of a respective said stator; and

at least two split blades, wherein each split blade is radially slidably mounted to a respective rotor, and each split blade comprises:

one or more rams, wherein each ram is adapted to be radially slidably disposed to the rotor; and

the two valve plates are respectively arranged at two end parts of the ejector rod in parallel, and each valve plate extends outwards along the ejector rod to form the split type blade with a penetrating ejector rod type structure; therefore, when the split blades drive the rotor to rotate under the action of the fluid, the ejector rod of each split blade slides radially relative to the rotor, so that the outer edge of each valve plate can always contact with the inner wall of the stator.

A pump device for converting mechanical energy into pressure energy of the second fluid during operation and outputting the second fluid; and

a coupling, wherein the coupling couples the fluid driving device to the pump device for transferring the mechanical energy converted by the fluid driving device to the pump device to drive the pump device to operate, so that the first fluid output by the fluid driving device can be mixed with the second fluid output by the pump device according to a predetermined ratio.

Further objects and advantages of the invention will be fully apparent from the ensuing description and drawings.

These and other objects, features and advantages of the present invention will become more fully apparent from the following detailed description, the accompanying drawings and the claims.

Drawings

Fig. 1 is a perspective view of a fluid driving device according to an embodiment of the present invention.

Fig. 2 shows an exploded view of the fluid driving device according to the above embodiment of the present invention.

Fig. 3 is a perspective view showing internal components of the fluid driving device according to the above-described embodiment of the present invention.

Fig. 4A to 4C respectively show cross-sectional views of internal members in the fluid drive device according to the above-described embodiment of the invention.

Fig. 5 is a perspective view schematically showing a rotor of the fluid driving device according to the above-described embodiment of the present invention.

Fig. 6A to 6C respectively show schematic cross-sectional views of the rotor in the fluid drive device according to the above-described embodiment of the invention.

Fig. 7 is a schematic view showing an operation principle of the fluid driving device according to the above-described embodiment of the present invention.

Fig. 8 is a perspective view illustrating a split blade of the fluid driving device according to the above embodiment of the present invention.

Fig. 9A and 9B show an example of the split blade according to the above embodiment of the present invention.

Fig. 10 shows a first variant embodiment of the split blade according to the above-described embodiment of the invention.

Fig. 11A and 11B show a second variant embodiment of the split blade according to the above-described embodiment of the invention.

Fig. 12A and 12B show a third variant embodiment of the split blade according to the above-described embodiment of the invention.

Fig. 13 to 16 show application examples of the split blade according to the above-described third modified embodiment of the present invention.

FIG. 17 is a schematic diagram of a fluid driven proportioner mixer in accordance with an embodiment of the invention.

Detailed Description

The following description is presented to disclose the invention so as to enable any person skilled in the art to practice the invention. The preferred embodiments in the following description are given by way of example only, and other obvious variations will occur to those skilled in the art. The basic principles of the invention, as defined in the following description, may be applied to other embodiments, variations, modifications, equivalents, and other technical solutions without departing from the spirit and scope of the invention.

It will be understood by those skilled in the art that in the present disclosure, the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in an orientation or positional relationship indicated in the drawings for ease of description and simplicity of description, and do not indicate or imply that the referenced devices or components must be constructed and operated in a particular orientation and thus are not to be considered limiting.

In the present invention, the terms "a" and "an" in the claims and the description should be understood as meaning "one or more", that is, one element may be one in number in one embodiment, and the element may be more than one in number in another embodiment. The terms "a" and "an" should not be construed as limiting the number unless the number of such elements is explicitly recited as one in the present disclosure, but rather the terms "a" and "an" should not be construed as being limited to only one of the number.

In the description of the present invention, it is to be understood that the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. In the description of the present invention, it should be noted that, unless explicitly stated or limited otherwise, the terms "connected" and "connected" are to be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Currently, existing hydro-motor blades are either conventional blades that are radially telescopically mounted to the rotor or are integral through-blades that are radially slidably mounted through the rotor. However, the conventional blade has the problem that the conventional blade cannot operate at a low rotating speed, and the integral penetrating blade generates large internal leakage and abrasion between the blade and a rotor due to low flatness and easy deformation, so that the performance and the service life of the conventional motor are seriously influenced. Therefore, the invention creatively provides a split type blade, which can solve the problem that the traditional blade cannot rotate at a low rotating speed and the problems of internal leakage and serious abrasion existing between the integrated penetrating blade and a rotor.

Referring to FIG. 9B of FIG. 1 of the drawings, a split blade according to an embodiment of the invention is illustrated. Specifically, the split blade 10 is used as a fitting of the fluid driving device 1, and is mounted on a rotor 20 of the fluid driving device 1 to convert pressure energy of a fluid into mechanical energy, wherein the split blade 10 may include one or more lift pins 11 and two valve plates 12. Each of said rams 11 is adapted to be radially slidably disposed to the rotor 20 of the fluid drive device 1. The two valve plates 12 are respectively mounted in parallel at two end portions 111 of the lift pin 11, and each valve plate 12 extends outwards along the lift pin 11 to form the split blades 10 having a through-pin structure, wherein when the split blades 10 drive the rotor 20 to rotate under the action of fluid, the lift pin 11 of each split blade 10 slides radially relative to the rotor 20, so that the outer edge 121 of each valve plate 12 can always contact the inner wall 31 of the stator 30 of the fluid driving device 1. It is understood that the fluid used in the fluid driving device 1 can be implemented as, but not limited to, liquid water such as fire water, river water, sea water, etc., and can also be implemented as other types of fluid such as solution, air, etc.

It is worth noting that compared with the traditional blade, the split blade 10 of the present invention is penetratingly arranged on the rotor 20 by the ejector rod 11, so that the split blade 10 can normally operate at any rotating speed, and the problem that the traditional blade cannot operate at a low speed is solved; compared with an integrated penetrating blade, the size of each valve plate 12 in the split blade 10 is far smaller than that of the integrated penetrating blade, so that the valve plates 12 can have high flatness even if being processed by adopting the same plate as the integrated penetrating blade, the risk of deformation of the valve plates 12 can be reduced, the abrasion between the valve plates 12 and the rotor 20 of the split blade 10 can be reduced, and the service life of the split blade 10 can be prolonged.

More specifically, in the above embodiment of the present invention, the lift pins 11 and the valve plate 12 in the split blade 10 are made of different materials, and the material strength of the lift pins 11 is greater than that of the valve plate 12, so that the cross-sectional area of the lift pins 11 can be much smaller than that of the valve plate 12 under the condition that the overall structure of the split blade 10 has sufficient strength, so as to greatly reduce the contact area between the lift pins 11 and the rotor 11, further reduce the wear between the lift pins 11 and the rotor 20 of the split blade 10, and improve the service life of the split blade 10. It can be understood that, since the existing one-piece through blade is usually made of a plastic plate material, the cross-sectional area of the connection portion in the one-piece through blade cannot be too small, but rather as large as possible, so as to ensure that the one-piece through blade has sufficient strength, so that the contact area between the one-piece through blade and the rotor is large, which not only increases the wear, but also causes serious liquid leakage.

Preferably, the lift pins 11 of the split blade 10 are made of a metal material such as stainless steel, carbon steel or alloy, which helps to improve the surface precision of the lift pins 11, so as to greatly reduce the gap between the lift pins 11 and the rotor 20, and further helps to reduce leakage between the split blade 10 and the rotor 20. It can be understood that, since the rotor 20 is also usually made of a metal material such as stainless steel, the matching degree of the rotor 20 and the carrier rod 11 can be improved by improving the machining precision, so as to greatly reduce the gap between the two and further reduce leakage.

It is noted that the valve sheet 12 of the split vane 10 of the present invention may be made of plastic or resin material such as PVDF (polyvinylidene fluoride) or PVC (polyvinyl chloride) to reduce abrasion and noise of the valve sheet 12 when the valve moves on the inner wall 31 of the stator 30. Of course, in other examples of the present invention, the valve plate 12 of the split vane 10 may also be made of other non-metallic materials, and the description of the present invention is omitted.

Illustratively, according to the above embodiment of the present invention, as shown in fig. 8, the split blade 10 may include three lifters 11 and two valve plates 12, wherein the three lifters 11 are uniformly spaced, and two end portions 111 of each lifter 11 are respectively connected to inner edge portions 122 of the two valve plates 12, so as to form the split blade 10 having a split lifter structure. Like this, two through three ejector pin 11 support ground is connected between the valve block 12 for the overall structure of split type blade 10 has high enough intensity, in case split type blade 10 takes place structural deformation, helps improving split type blade 10's quality and life.

It should be noted that although the split blade 10 of fig. 1 to 8 and the following description illustrate the features and advantages of the split blade 10 of the present invention by taking the split blade 10 including three lifters 11 as an example, those skilled in the art will understand that the specific structure of the split blade 10 disclosed in fig. 1 to 8 and the following description is only an example and does not limit the content and scope of the present invention, for example, in other examples of the split blade 10, the number of the lifters 11 may be one or two, and certainly may be more than three, to meet different requirements.

Specifically, in one example of the present invention, as shown in fig. 9A and 9B, the valve sheet 12 of the split blade 10 is detachably mounted to the end 111 of the carrier rod 11, so as to repair or replace the split blade 10.

More specifically, as shown in fig. 9A and 9B, the inner edge 122 of the valve plate 12 of the split vane 10 is provided with one or more fitting grooves 1220, wherein the end 111 of the plunger 11 can be inserted into the fitting groove 1220 of the inner edge 122 of the valve plate 12, so as to connect the valve plate 12 and the plunger 11.

For example, as shown in fig. 9A, the lift pin 11 of the two-piece vane 10 can be flexibly connected to the valve plate 12, for example, the lift pin 11 and the valve plate 12 are connected by a fastener 151 (e.g., a screw). For example, the end portion 111 of the lift pin 11 of the split vane 10 is provided with a screw fitting head, and the inner side portion 122 of the valve plate 12 of the split vane 10 is provided with a screw fitting groove, so that the screw fitting head of the end portion 111 of the lift pin 11 is inserted into the screw fitting groove of the inner side portion 122 of the valve plate 12, thereby flexibly and fixedly mounting the valve plate 12 to the end portion 111 of the lift pin 11 by means of screw connection.

It should be noted that in another example of the present invention, the lift pin 11 and the valve plate 12 may be flexibly connected through a spring member. Specifically, the split blade 10 further comprises one or more micro springs, wherein each micro spring is supportedly connected between the lift rod 11 and the valve plate 12, so as to achieve the free expansion and contraction fine adjustment of the valve plate 12 through the micro spring.

Of course, in other examples of the present invention, the lift pin 11 of the split vane 10 can be rigidly connected to the valve plate 12, i.e. the lift pin 11 and the valve plate 12 are tightly fitted (e.g. interference fit). For example, as shown in fig. 10, a first modified embodiment of the split blade 10 according to the present invention is illustrated, specifically, the end portion 111 of the ejector 11 of the split blade 10 is provided with an interference fit head, and the inner edge portion 122 of the valve plate 12 of the split blade 10 is provided with an interference fit groove, so that the interference fit head of the end portion 111 of the ejector 11 is inserted into the interference fit groove of the inner edge portion 122 of the valve plate 12 with a tight fit, so as to achieve rigid connection and installation of the valve plate 12 on the end portion 111 of the ejector 11.

Preferably, as shown in fig. 8 and 9B, the lift pins 11 of the split vane 10 have a circular cross-section to minimize the outer surface area of the lift pins 11, i.e., the contact area between the lift pins 11 and the rotor 20, in case the lift pins 11 have sufficient strength, thereby reducing wear and leakage between the lift pins 11 and the rotor 20. Of course, in other examples of the present invention, the top bar 11 may have a cross section such as an oval shape, a rounded rectangle, etc., and the present invention will not be described in detail herein.

Illustratively, the lift pins 11 of the split blade 10 have two end portions 111 and an intermediate portion 112 integrally connecting the two end portions 111, and the cross section of the intermediate portion 112 is circular and the same as the cross section of the end portions 111, that is, the intermediate portion 112 of the lift pin 11 integrally extends from one end portion 111 of the lift pin 11 to the other end portion 111 of the lift pin 11 with an equal cross section, so as to form the lift pin 11 having a cylindrical structure.

It is to be noted that, as shown in fig. 4A and 7, the stator 30 of the fluid drive device 1 is divided into an inlet region 301, a positive displacement region 302, an outlet region 303, and a negative displacement region 304 in this order along the rotation direction of the rotor 12 (counterclockwise direction as shown in fig. 7), wherein the envelope curves of the inner wall 31 of the stator 30 at the positive displacement region 302 and the negative displacement region 304 are implemented as concentric circular arc curves, and the radius of curvature of the envelope curve of the inner wall 31 of the stator 30 at the positive displacement region 302 is larger than the radius of curvature of the envelope curve at the negative displacement region 304. Furthermore, the envelope of the inner wall 31 of the stator 30 at the inlet region 301 and the outlet region 303 may be implemented as a transition curve, such as a plane curve like a circular arc, an archimedean spiral, a pascal spiral, or a logarithmic equation curve, etc., to form the inner cavity 300 having a non-circular structure inside the stator 30.

Preferably, as shown in fig. 7, the outer edge portion 121 of the valve plate 12 of the segment vane 10 has an arc-shaped end surface 1210, and the arc-shaped end surface 1210 of the valve plate 12 has a double curvature radius arc structure, wherein when the valve plate 12 of the segment vane 10 slides at the positive displacement region 302 or the negative displacement region 304 of the inner wall 31 of the stator 30, an arc portion with a larger curvature radius on the arc-shaped end surface 1210 of the valve plate 12 contacts with the inner wall 31 of the stator 30; when the valve plate 12 of the split vane 10 slides in the inlet area 301 or the outlet area 303 of the inner wall 31 of the stator 30, the arc part with the smaller curvature radius on the arc end surface 1210 of the valve plate 12 contacts with the inner wall 31 of the stator 30, which helps to reduce the wear between the valve plate 12 of the split vane 10 and the stator 30.

More preferably, the curvature radius of the arc-shaped part with the larger curvature radius on the arc-shaped end surface 1210 of the valve plate 12 of the split vane 10 is equal to the curvature radius of the envelope curve of the inner wall 31 of the stator 30 at the negative displacement region 304, so that the valve plate 12 of the split vane 10 and the inner wall 31 of the stator 30 make surface contact at the negative displacement region 304, so as to reduce the gap between the valve plate 12 of the split vane 10 and the inner wall 31 of the stator 30 at the negative displacement region 304 while better guiding the valve plate 12 of the split vane 10 to slide along the inner wall 31 of the stator 30, thereby reducing liquid leakage.

For example, as shown in fig. 7, the arc end surface 1210 of the valve plate 12 of the split vane 10 includes a front end surface 1211, a rear end surface 1212, and an intermediate end surface 1213 located between the front end surface 1211 and the rear end surface 1212, wherein the front end surface 1211 of the valve plate 12 faces the rotation direction of the rotor 20, and the rear end surface 1212 of the valve plate 12 faces away from the rotation direction of the rotor 20, the radius of curvature of the front end surface 1211 and the radius of curvature of the rear end surface 1212 are the same and smaller than the radius of curvature of the intermediate end surface 1213, and the radius of curvature of the intermediate end surface 1213 is equal to the radius of curvature of the envelope curve of the inner wall 31 of the stator 30 at the negative displacement region 304. It is understood that the rotation direction of the rotor 20 of the present invention is implemented in a direction from the rear end surface 1212 of the valve plate 12 to the front end surface 1211 of the valve plate 12.

In this way, when the outer edge portion 121 of the valve sheet 12 of the segment vane 10 is located at the inlet region 301 of the stator 30, the rear end surface 1212 of the valve sheet 12 contacts the inner wall surface 31 of the stator 30; when the outer edge 121 of the valve plate 12 of the split vane 10 is in the outlet region 303 of the stator 30, the front end surface 1211 of the valve plate 12 contacts with the inner wall 31 of the stator 30; when the outer edge 121 of the valve sheet 12 of the segment vane 10 is located in the positive displacement region 302 and the negative displacement region 304 of the stator 30, the middle end surface 1213 of the valve sheet 12 contacts the inner wall 31 of the stator 30; this allows the position of the valve plate 12 of the split vane 10 in contact with the stator 30 to be changed at different regions of the stator 11, which helps to reduce the wear of the split vane 10 and prolong the service life of the fluid driving device 1. It can be understood that, because the radius of curvature of the front end surface 1211 and the rear end surface 1212 of the valve plate 12 is smaller, the clearance between the valve plate 12 and the inner wall 31 of the stator 30 at the inlet area 301 and the outlet area 303 is larger, the contact area is smaller, and the wear between the split blade 10 and the stator 30 is greatly reduced; since the curvature radius of the middle end surface 1213 of the valve sheet 12 is large, the clearance between the valve sheet 12 and the inner wall 31 of the stator 30 at the positive displacement area 302 and the negative displacement area 304 is small, and the contact area is large, which not only helps to guide the split blades 10 to slide along the inner wall 31 of the stator 30, but also can reduce the internal leakage of the fluid driving device 1.

It should be noted that, in other examples of the present invention, the arc-shaped end surface 1210 of the valve plate 12 of the split vane 10 may also have a single-radius-of-curvature arc structure, and the radius of curvature of the arc-shaped end surface 1210 is preferably equal to the radius of curvature of the envelope curve of the inner wall 31 of the stator 30 at the negative displacement region 304; that is, the front end surface 1211, the rear end surface 1212, and the intermediate end surface 1213 of the arc-shaped end surface 1210 of the valve sheet 12 have the same radius of curvature, and are equal to the radius of curvature of the envelope curve of the inner wall 31 of the stator 30 at the negative displacement region 304.

In addition, because the envelope curves of the stator 30 at the positive displacement area 302 and the negative displacement area 304 are circular arc curves, the split vane 10 does not have a swing angle when the split vane 30 is in valve motion at the positive displacement area 302 and the negative displacement area 304 of the stator 30, so that the contact position of the split vane 10 and the stator 30 at the positive displacement area 302 and the negative displacement area 304 is always at the middle end surface 1213 of the valve plate 12 of the split vane 10, and further the outer edge 121 of the valve plate 12 of the split vane 10 is seriously worn at the middle end surface 1213, which easily causes the fluid driving device 1 to generate internal leakage and causes pressure energy loss of the fluid.

Therefore, in the above embodiment of the present invention, as shown in fig. 7 and 8, the split vane 10 further includes at least two elastic members 13, wherein each elastic member 13 is correspondingly disposed on the middle end surface 1213 of the outer edge portion 121 of the valve plate 12, and the elastic members 13 are located between the valve plate 12 and the inner wall 31 of the stator 30 to perform a sealing function when the valve plate 12 of the split vane 10 is located in the positive displacement region 302 and the negative displacement region 304 of the stator 30. In other words, the elastic member 13 can seal the gap between the split blades 10 and the stator 30, prevent the fluid from directly leaking from the inlet area 301 of the stator 30 to the outlet area 303 of the stator 30, and effectively reduce the internal leakage and the wear of the fluid driving device 1, so as to reduce the pressure energy loss of the fluid as much as possible. It is understood that the elastic member 13 may be made of, but not limited to, a material having a certain elastic deformation, such as rubber, plastic, polymer material, metal material, etc., and the elastic member 13 may be implemented as an elastic member, such as an elastic strip, an O-ring, a circular pad, an arc strip, a T-shaped strip, etc., as long as it can achieve a sealing effect to reduce the internal leakage, which will not be described in detail herein.

It should be noted that, in the above embodiment of the present invention, in order to mount the valve plate 12 to the end portion 111 of the stem 11, the fitting groove 1220 is generally provided at a portion of the inner edge portion 122 of the valve plate 12 connected to the stem 11 so as to be insertedly connected to the end portion 111 of the stem 11. However, the strength of the portion of the inner edge 122 of the valve plate 12 connected to the lift rod 11 is weakened due to the fitting groove 1220, so that the valve plate 12 is easily deformed or broken at the position, and the performance and the service life of the split blade 1 are affected, therefore, the portion of the valve plate 12 connected to the lift rod 11 can be reinforced, so as to improve the overall strength of the split blade 10.

Specifically, as shown in fig. 11A and 11B, a second modified embodiment of the split blade 10 according to the above-described embodiment of the present invention is illustrated. Compared to the above described embodiment of the invention, the split blade 10 according to this variant embodiment of the invention differs in that: the split blade 10 further includes one or more reinforcing elements 14, wherein the reinforcing elements 14 are correspondingly disposed at the positions of the valve plate 12 connected to the lift pins 11, so as to reinforce the connection strength between the valve plate 12 and the lift pins 11 and improve the overall strength of the split blade 10. In other words, the reinforcing member 14 is disposed outside the fitting groove 1220 of the valve sheet 12 to improve the structural strength of the valve sheet 12 at the fitting groove 1220.

More specifically, as shown in fig. 11A and 11B, the reinforcing member 14 of the segment vane 10 may be implemented as a pair of reinforcing ribs 141, wherein the pair of reinforcing ribs 141 are symmetrically disposed at front and rear sides of the fitting groove 1220 of the valve plate 12, and each of the reinforcing ribs 141 extends from the inner side portion 122 of the valve plate 12 to the outer side portion 121 of the valve plate 12 to reinforce the overall strength of the valve plate 12, which helps prevent the valve plate 12 from being deformed or broken.

Preferably, as shown in fig. 11B, the reinforcing rib 141 integrally extends outward from the valve sheet 12 to increase the wall thickness of the fitting groove 1220, thereby reinforcing the strength of the valve sheet 12 at the fitting groove 1220.

Of course, in other examples of the present invention, the reinforcing element 14 of the two-piece vane 10 can also be implemented as a rib 141, wherein the rib 141 is correspondingly disposed at the front side or the rear side of the fitting groove 1220 of the valve plate 12, and still has the effect of reinforcing the strength of the valve plate 12. However, if the rib 141 is provided only at one side of the fitting groove 1220 of the valve plate 12, the other side of the fitting groove 1220 of the valve plate 12 cannot be reinforced and is easily broken.

Further, as shown in fig. 12A and 12B, a third modified embodiment of the split blade 10 according to the above embodiment of the present invention is illustrated. Compared to the above-described second variant embodiment of the invention, the split blade 10 according to this variant embodiment of the invention differs in that: the reinforcing member 14 of the segment vane 10 is implemented as one of the reinforcing ribs 141 provided at the rear side of the valve plate 12, and the fitting groove 1220 of the valve plate 12 is eccentrically provided rearward at the inner side portion 122 of the valve plate 12, so that the fitting groove 1220 is located at the junction of the inner side portion 122 of the valve plate 12 and the reinforcing rib 141, so that the wall thickness of the fitting groove 1220 is increased, thereby achieving an effect of reinforcing the valve plate 12 in all directions only by one of the reinforcing ribs 141.

It is noted that, since the fitting grooves 1220 on each valve plate 12 are offset backward, so that the centers of the fitting grooves 1220 will be offset from the central axis of the split blade 10, the end portions 111 of the lift pins 11 of the split blade 10 will also be offset backward from the central axis of the split blade 10 so as to be aligned with the corresponding fitting grooves 1220, which results in that the center lines of the two end portions 111 of the lift pins 11 are not in the same line.

Preferably, as shown in fig. 12B, the cross-sectional area of the middle portion 112 of the lift pin 11 of the split blade 10 is larger than the cross-sectional area of the end portion 111 of the lift pin 11, and the two end portions 111 of the lift pin 11 integrally extend outward from the opposite ends of the middle portion 112 along a direction parallel to the center line of the middle portion 112, respectively, so that the two end portions 111 of the lift pin 11 are offset toward the rear side of the corresponding valve sheet 12, respectively. Of course, in other examples of the present invention, the cross-sectional area of the middle portion 112 of the post 11 may also be equal to the cross-sectional area of the end portion 111 of the post 11, and it is only necessary to extend the middle portion 112 of the post 11 from one end portion 111 of the post 11 to the other end portion 111 in an inclined or bent manner, which is not described again in the present invention.

According to another aspect of the present invention, the present invention further provides a fluid driving device 1 for converting pressure energy of a fluid into mechanical energy. Specifically, as shown in fig. 1 to 9B, the fluid driving device 1 may include at least one stator 30, at least one rotor 20, and at least two split blades 10, wherein each stator 30 has an inner cavity 300, and each rotor 20 is rotatably disposed in the inner cavity 300 of the corresponding stator 30; wherein each of said split blades 10 is radially slidably mounted to said rotor 20. The split vane 10 includes one or more lifters 11 and two valve plates 12. Each of the rams 11 is adapted to be radially slidably disposed through the rotor 20. The two valve plates 12 are respectively mounted at two end portions 111 of each lift pin 11 in parallel, and each valve plate 12 extends outwards along the lift pin 11 to form the split type blade 10 with a through-pin structure, wherein when the split type blade 10 drives the rotor 20 to rotate under the action of the fluid, the lift pin 11 of each split type blade 10 slides radially relative to the rotor 20, so that the outer edge 121 of each valve plate 12 can always contact the inner wall 31 of the stator 30.

More specifically, as shown in fig. 4A to 4C, the rotor 20 of the fluid driving device 1 has at least two through holes 21, wherein each through hole 21 extends along a radial direction of the rotor 20 to penetrate through the rotor 20 for slidably mounting the split blades 10 such that the split blades 10 can slide radially in the through hole 21 to ensure that the outer edge portion 121 of the valve sheet 12 of the split blade 10 can valve on the inner wall 31 of the stator 30. It should be noted that the at least two through holes 21 are preferably distributed at equal intervals on the rotor 20, so that the distance between the valve plates 12 of the split blades 10 installed on the through holes 21 is kept the same, thereby ensuring stable operation of the fluid driving device 1.

Preferably, as shown in fig. 6A to 6C, each of the through holes 21 of the rotor 20 includes one or more sliding holes 211 and two telescopic slots 212, wherein two of the telescopic slots 212 are symmetrically located at the outer circumference of the rotor 20, and the sliding holes 211 extend from one of the telescopic slots 212 to the other telescopic slot 212 to communicate with the two telescopic slots 212, thereby forming the through hole 21 penetrating through the rotor 20. In other words, when the split blade 10 is mounted to the through hole 21 of the rotor 20, the plunger 11 of the split blade 10 is slidably located in the sliding hole 211 of the rotor 20, and the valve sheet 12 of the split blade 10 is telescopically located in the telescopic groove 212 of the rotor 20; that is, the knock bar 11 of the split vane 10 is slidably mounted to the sliding hole 211 of the rotor 20, and the valve sheet 12 of the split vane 10 is telescopically mounted to the telescopic groove 212 of the rotor 20 to radially slidably mount the split vane 10 to the through hole 21 of the rotor 20. Thus, when the rotor 20 rotates relative to the stator 30, the lift pins 11 of the split blades 10 slide radially in the sliding holes 211 of the rotor 20, and at the same time, the valve plates 12 of the split blades 10 extend or retract into the telescopic slots 212 of the rotor 20, so as to ensure that the outer edge portions 121 of the valve plates 12 of the split blades 10 valve on the inner wall 31 of the stator 30.

Further, as shown in fig. 4A to 4C, the rotor 20 of the fluid driving device 1 may further have at least two pairs of sealing grooves 22, wherein each pair of sealing grooves 22 is correspondingly disposed on a sidewall (e.g., a front sidewall) of two of the telescopic grooves 212 of the through hole 21, for accommodating a sealing member (not shown in the drawings) to seal a gap between the valve plate 12 of the split blade 10 and the rotor 20 by the sealing member, so as to prevent fluid from leaking from the gap between the valve plate 12 of the split blade 10 and the rotor 20, and reduce internal leakage of the fluid driving device 1.

Further, the rotor 20 of the fluid driving device 1 may also include one or more bushings (not shown), wherein the bushings are adapted to be mounted to the sliding holes 211 of the through holes 21 of the rotor 20, and the bushings surround the tappets 11 of the split blades 10 to substantially reduce the gap between the tappets 11 and the rotor 20, thereby preventing fluid from leaking from the gap between the tappets 11 of the split blades 10 and the rotor 20, and thus minimizing internal leakage of the fluid driving device 1.

It is worth mentioning that since the segment blades 10 only slide radially at the inlet area 301 and the outlet area 302 of the stator 30, but not at the positive displacement area 302 and the negative displacement area 304 of the stator 30, only the segment blades 10 sliding at the inlet area 301 and the outlet area 302 of the stator 30 will wear with the rotor 20. At the inlet area 301 and the outlet area 302, the pressure difference between the front side and the rear side of the valve plate 12 of the split vane 10 is large, which increases the wear between the split vane 10 and the rotor 20.

In order to solve this problem, in the above example of the present invention, as shown in fig. 4A to 6C, the rotor 20 of the fluid driving device 1 is further provided with a plurality of balance holes 23, wherein each balance hole 23 is located between adjacent telescopic slots 212 and is communicated with a corresponding one of the telescopic slots 212, so that when the valve plate 12 of the split vane 10 slides to the inlet area 301 and the outlet area 303 of the stator 30, the balance holes 23 are used for introducing a fluid into the corresponding telescopic slot 212 to balance a pressure difference across the valve plate 12, so that the pressures across the split vane 10 are substantially balanced at the inlet area 301 and the outlet area 303 of the stator 30, thereby reducing wear between the split vane 10 and the rotor 20.

Illustratively, as shown in fig. 4A to 4C, four balancing holes 23 are provided on the rotor 20 of the fluid driving device 1 of the present invention, and each balancing hole 23 is communicated with the bottom of the telescopic slot 212 located at the front side of the balancing hole 23, so as to introduce the fluid located at the rear side of the valve plate 12 of the split vane 10 into the telescopic slot 212 through the balancing hole 23, so that the water pressure is introduced into the front and rear sides of the valve plate 12 of the split vane 10, thereby balancing the pressure difference between the front and rear sides of the split vane 10, reducing the wear, and prolonging the service life of the split vane 10 and thus the entire fluid driving device 1. Of course, in other examples of the present invention, the balance hole 23 may communicate with other parts of the telescopic slot 212, as long as the communicating part is located inside the seal groove 22 in the telescopic slot 212 (that is, the connecting part of the balance hole 23 and the telescopic slot 212 is closer to the central axis of the rotor 20 than the seal groove 22), so as to ensure that the fluid can balance the pressure difference between the front side and the rear side of the valve plate 12 of the split vane 10 under the sealing effect of the seal groove 22, which is not described in detail herein.

According to the above embodiment of the present invention, as shown in fig. 1 and 2, the fluid driving device 1 may further include a housing 40 and two end plates 50, wherein the housing 40 has an inlet pipe 41 for an inflow of a fluid and an outlet pipe 42 for an outflow of the fluid, wherein the stator 30 is fixedly disposed in the housing 40, and the rotor 20 is rotatably mounted in the housing 40 by the end plates 50, wherein the inlet pipe 41 of the housing 40 corresponds to the inlet 32 of the stator 30, and the outlet pipe 42 of the housing 40 corresponds to the outlet 33 of the stator 30, so that the fluid enters the inner cavity 300 of the stator 30 through the inlet pipe 41 of the housing 40 via the inlet 32 of the stator 30; and then out through the outlet tube 42 of the housing 40 via the outlet 33 of the stator 30. Meanwhile, the fluid drives the split blades 10 to rotate, so as to drive the rotor 20 to rotate, so that the pressure energy of the fluid is partially converted into mechanical energy, and a device such as a plunger pump, a fan and the like can be driven to rotate through the rotor 20, so as to achieve a corresponding effect.

Preferably, the inlet 32 of the stator 30 of the present invention may be implemented as a grid port, and the grid port is uniformly distributed with the inlet area 301 of the stator 30, so that the fluid flowing in through the inlet 32 of the stator 30 can simultaneously flow to both sides of the valve sheet 12 of the split vane 10 at the inlet area 301, so that the pressures on both sides of the split vane 10 are further balanced at the inlet area 301 of the stator 30, thereby minimizing the wear between the split vane 10 and the rotor 20. Of course, the outlet openings 33 of the stator 30 of the invention may also be embodied as grid openings which are evenly distributed over the outlet area 303 of the stator 30.

It should be noted that, in the third modified embodiment of the present invention, since the split vane 10 is provided with one of the ribs 141 on the rear side of the valve plate 12, that is, the rib 141 of the split vane 10 adopts an eccentric structure design, in order to enable the split vane 10 to slide radially relative to the rotor 20, the through hole 21 on the rotor 20 of the fluid driving device 1 is matched with the structure of the split vane 10, for example, the through hole 21 may further have an eccentric groove 213 corresponding to the rib 141, wherein the eccentric groove 213 is formed by extending backwards from the telescopic groove 212 and is used for slidably receiving the rib 141, see fig. 15 and 16 of the drawings of the specification of the present invention, and the present invention is not repeated herein.

In the second modified embodiment of the present invention, the ribs 141 of the split vane 10 are designed to be concentric, that is, each pair of ribs 141 is symmetrically disposed on the front and rear sides of the valve plate 12. Therefore, the through hole 21 may further have a concentric groove corresponding to each pair of the reinforcing ribs 141, wherein the concentric groove extends from the expansion groove 212 to both front and rear sides simultaneously for slidably receiving the reinforcing ribs 141.

According to another aspect of the present invention, there is further provided a fluid driven proportioner for mixing a first fluid and a second fluid in a predetermined ratio. Specifically, as shown in fig. 17, the fluid driven proportioner comprises the fluid driving device 1, a pump device 2 and a coupling 3, and the coupling 3 couples the fluid driving device 1 to the pump device 2, wherein when the first fluid (such as fire water and the like) flows into the fluid driving device 1, first, the fluid driving device 1 partially converts the pressure energy of the first fluid into mechanical energy and outputs the first fluid; then, the coupling 3 transmits the mechanical energy converted by the fluid driving device 1 to the pump device 2, and finally, the pump device 2 converts the mechanical energy transmitted by the coupling 3 into pressure energy of a second fluid (such as foam concentrate and the like) to output the second fluid, so that the first fluid and the second fluid can be mixed according to the predetermined ratio. It is understood that the predetermined ratio mentioned in the present invention may be implemented as various ratio ranges such as, but not limited to, 1%, 3%, or 6%, for example, when the predetermined ratio is implemented as a ratio range of 3%, the predetermined ratio may be between 3% and 3.9%.

Preferably, the pump device 2 can be, but is not limited to, implemented as a reciprocating plunger pump, wherein the reciprocating plunger pump performs reciprocating motion under the driving of the fluid driving device 1 through the coupler 3 to suck the second fluid and inject the second fluid into the first fluid under pressure to realize proportional mixing of the first fluid and the second fluid. It is understood that the pump device 2 may also be implemented as other types of pumps, such as centrifugal, axial, partial or vortex pumps, etc.

According to the above embodiment of the present invention, as shown in fig. 17, the fluid driven proportioner further comprises a piping arrangement 4, wherein the piping arrangement 4 may comprise a mixing line and a purge line. The mixing pipeline is used for communicating an outlet of the reciprocating plunger pump with an outlet of the fluid driving device 1 and conveying the second fluid conveyed by the reciprocating plunger pump to the outlet of the fluid driving device 1 through the mixing pipeline, so that the second fluid conveyed by the reciprocating plunger pump is proportionally mixed with the first fluid conveyed by the fluid driving device 1. The cleaning pipeline is used for communicating the inlet of the reciprocating plunger pump with the inlet of the fluid driving device 1 and conveying the first fluid from the inlet of the fluid driving device 1 to the inlet of the reciprocating plunger pump, and then the reciprocating plunger pump and the mixing pipeline are cleaned through the first fluid before mixing begins or after mixing is completed.

It is understood that the mixing pipeline and/or the cleaning pipeline may be provided with various pipeline auxiliary devices such as a manual ball valve, a check valve, an exhaust valve, a pressure gauge, or an instrument valve, but not limited thereto, and only the cleaning requirement is satisfied, and the present invention is not described in detail herein.

In summary, the fluid driven proportioner of the invention also has the following advantages:

1) hydraulic drive, not sluicing, need not extra power: the proportional mixer can be directly driven by fire fighting water, additional power such as a motor or a diesel engine is not needed, the proportional mixer is different from a pelton turbine, water is not drained, a special drainage ditch is not needed, the proportional mixer can work as long as a fire fighting main pump runs normally, and the reliability of the whole system is greatly improved.

2) Positive pressure injection, no back pressure requirement: the plunger pump can pressurize the foam concentrate, so that the pressure of an injection point is slightly higher than the water pressure, therefore, the plunger pump has no back pressure requirement in a pressure range, is suitable for any type of system, and can realize remote injection.

3) The liquid absorption capacity is strong, and the method is suitable for all fire extinguishing agents: the plunger pump has super-strong self-absorption capacity, is not only suitable for all foam extinguishing agents with high viscosity, anti-solubility and no fluorine, but also suitable for all water-based extinguishing agents such as wetting agents, decontamination agents and other various medicaments, and has the highest viscosity of 10000 cps.

4) The flow range is wide, and the device is not influenced by the water supply pressure and back pressure: the fluid driving device 1 and the reciprocating plunger pump are both of a positive displacement type, so that the proportioning mixer has a quite wide flow range within a certain working pressure range and is not influenced by the water supply pressure and back pressure.

5) Can be installed at any position, has no requirement of a straight pipe section: the system can be directly installed on a main water supply loop, various installation directions exist, the proportional mixer is more flexible and convenient to install, and the outlet of the system does not have the requirement of a straight pipe section.

6) The response speed is high: as soon as water flows through the fluid driving device 1, the reciprocating plunger pump can be driven and foam concentrate and water are sucked for proportional mixing, and an accurate mixing ratio is instantly achieved.

It will be appreciated by persons skilled in the art that the embodiments of the invention described above and shown in the drawings are given by way of example only and are not limiting of the invention. The objects of the invention have been fully and effectively accomplished. The functional and structural principles of the present invention have been shown and described in the examples, and any variations or modifications of the embodiments of the present invention may be made without departing from the principles.