阅读说明：本技术 泵体和心室辅助系统 (Pump body and ventricular assist system ) 是由 余顺周 于 2020-11-18 设计创作，主要内容包括：本申请属于医疗器械技术领域,尤其涉及一种泵体和心室辅助系统,泵体包括泵壳和叶轮,泵壳形成腔室,开设有入液口,腔室两腔壁上形成液力轴承,液力轴承具有多个第一动压槽和第二动压槽,第一动压槽和第二动压槽绕入液口中心轴线交替排布,第一动压槽长度大于第二动压槽,第一动压槽靠近入液口中心轴线一端位于第一圆,远离入液口的中心轴线一端的端部位于第二圆,第二动压槽靠近入液口的中心轴线一端的端部位于第三圆,第一圆、第二圆及第三圆的圆心位于入液口中心轴线上,第三圆半径大于第一圆半径,且小于第二圆半径。上述泵体的叶轮磨损率较低且使用可靠性较高。(The utility model belongs to the technical field of medical instrument, especially, relate to a pump body and ventricle auxiliary system, the pump body includes pump case and impeller, the pump case forms the cavity, seted up into the liquid mouth, form hydraulic bearing on the two chamber walls of cavity, hydraulic bearing has a plurality of first dynamic pressure grooves and second dynamic pressure groove, first dynamic pressure groove and second dynamic pressure groove are arranged around going into liquid mouth the central axis in turn, first dynamic pressure groove length is greater than second dynamic pressure groove, first dynamic pressure groove is close to income liquid mouth the central axis one end and is located first circle, the tip of keeping away from the central axis one end of going into the liquid mouth is located the second circle, the tip that second dynamic pressure groove is close to the central axis one end of going into the liquid mouth is located the third circle, first circle, the centre of a circle of second circle and third circle is located income liquid mouth central axis, the third circle radius is greater than first circle radius, and be less than the second circle radius. The impeller of the pump body is low in wear rate and high in use reliability.)

1. A pump body, characterized by: the pump body comprises a pump shell and an impeller, a cavity is formed in the pump shell, a liquid inlet communicated with the cavity is further formed in the pump shell, the impeller can be suspended and rotated in the cavity, and centrifugal force for conveying fluid media can be generated when the impeller rotates; wherein the chamber is provided with a hydrodynamic bearing on two opposite chamber walls on the central axis of the liquid inlet, the hydrodynamic bearing is provided with a plurality of first dynamic pressure grooves and a plurality of second dynamic pressure grooves, the plurality of first dynamic pressure grooves and the plurality of second dynamic pressure grooves are alternately arranged around the central axis of the liquid inlet at intervals, the length of the first dynamic pressure grooves is greater than that of the second dynamic pressure grooves, the end parts of the plurality of first dynamic pressure grooves, which are close to one end of the central axis of the liquid inlet, are all located on a first circle, the end parts of the plurality of first dynamic pressure grooves, which are far away from one end of the central axis of the liquid inlet, are all located on a second circle, the end parts of the plurality of second dynamic pressure grooves, which are close to one end of the central axis of the liquid inlet, are all located on a third circle, and the centers of the first circle, the second circle and the third circle are all located on the central axis of the liquid inlet, the radius of the third circle is larger than the radius of the first circle and smaller than the radius of the second circle.

2. The pump body according to claim 1, characterized in that: each of the first dynamic pressure generating grooves and each of the second dynamic pressure generating grooves have an equiangular spiral shape.

3. The pump body according to claim 1, characterized in that: the hydraulic bearings on the two cavity walls are arranged in mirror symmetry.

4. The pump body according to claim 1, characterized in that: the end parts of one ends of the second dynamic pressure grooves, which are far away from the central axis of the liquid inlet, are all positioned on a fourth circle, and the radius of the fourth circle is equal to that of the second circle.

5. The pump body according to claim 1, characterized in that: the first circle is bisected by an end portion of one end of the plurality of first dynamic pressure grooves which is closer to the center axis of the liquid inlet, the second circle is bisected by an end portion of one end of the plurality of first dynamic pressure grooves which is farther from the center axis of the liquid inlet, and the third circle is bisected by an end portion of one end of the plurality of second dynamic pressure grooves which is closer to the center axis of the liquid inlet.

6. The pump body according to claim 1, characterized in that: in each of the hydrodynamic bearings, the second dynamic pressure groove is provided between every adjacent two of the first dynamic pressure grooves.

7. The pump body according to any one of claims 1 to 6, wherein: the width of the first dynamic pressure groove and the width of the second dynamic pressure groove are gradually increased from one end close to the central axis of the liquid inlet to one end far away from the central axis of the liquid inlet.

8. The pump body according to any one of claims 1 to 6, wherein: and one end of the first dynamic pressure groove, which is close to the central axis of the liquid inlet, and one end of the first dynamic pressure groove, which is far away from the central axis of the liquid inlet, are provided with chamfers, and/or one end of the second dynamic pressure groove, which is close to the central axis of the liquid inlet, and one end of the second dynamic pressure groove, which is far away from the central axis of the liquid inlet, are provided with chamfers.

9. A pump body, characterized by: the impeller is capable of rotating in a suspended manner, centrifugal force for conveying fluid media can be generated when the impeller rotates, the impeller is provided with a first side and a second side which are respectively opposite to the two cavity walls, hydrodynamic bearings are respectively formed on the first side and the second side, each hydrodynamic bearing is provided with a plurality of first dynamic pressure grooves and a plurality of second dynamic pressure grooves, the plurality of first dynamic pressure grooves and the plurality of second dynamic pressure grooves of each hydrodynamic bearing are alternately arranged around the rotating axis of the impeller at intervals, the length of each first dynamic pressure groove is greater than that of each second dynamic pressure groove, and the end parts of the first dynamic pressure grooves, which are close to one end of the rotating axis of the impeller, are positioned on a first circle, the end part of one end of the first dynamic pressure groove far away from the rotation axis of the impeller and the end part of one end of the second dynamic pressure groove far away from the rotation axis of the impeller are both positioned on a second circle, the first circle and the second circle are concentric, and the circle center is positioned on the rotation axis of the impeller.

10. A ventricular assist system, characterized by: comprising a blood pump comprising a pump body as claimed in any one of claims 1 to 8 or a pump body as claimed in claim 9.

Technical Field

The application belongs to the technical field of medical equipment, especially, relate to a pump body and ventricle auxiliary system.

Background

The pump body can drive fluid medium flow through the impeller that sets up in it, and to current magnetic suspension pump body, the impeller often can collide and take place wearing and tearing with the chamber wall of the pump body when the operation, and the impeller is its key part, directly influences the life and the reliability of the pump body, and blood pump especially, impeller and the chamber wall of the pump body take place to rub and still can cause the damage to blood.

Disclosure of Invention

An object of the embodiment of this application is to provide a lower and the higher pump body of reliability of using of impeller wear rate.

In order to achieve the purpose, the technical scheme adopted by the application is as follows:

in a first aspect: providing a pump body, wherein the pump body comprises a pump shell and an impeller, a cavity is formed in the pump shell, a liquid inlet communicated with the cavity is further formed in the pump shell, the impeller can be suspended and rotated in the cavity, and centrifugal force for conveying fluid media can be generated when the impeller rotates; wherein the chamber is provided with a hydrodynamic bearing on two opposite chamber walls on the central axis of the liquid inlet, the hydrodynamic bearing is provided with a plurality of first dynamic pressure grooves and a plurality of second dynamic pressure grooves, the plurality of first dynamic pressure grooves and the plurality of second dynamic pressure grooves are alternately arranged around the central axis of the liquid inlet at intervals, the length of the first dynamic pressure grooves is greater than that of the second dynamic pressure grooves, the end parts of the plurality of first dynamic pressure grooves, which are close to one end of the central axis of the liquid inlet, are all located on a first circle, the end parts of the plurality of first dynamic pressure grooves, which are far away from one end of the central axis of the liquid inlet, are all located on a second circle, the end parts of the plurality of second dynamic pressure grooves, which are close to one end of the central axis of the liquid inlet, are all located on a third circle, and the centers of the first circle, the second circle and the third circle are all located on the central axis of the liquid inlet, the radius of the third circle is larger than the radius of the first circle and smaller than the radius of the second circle.

Alternatively, each of the first dynamic pressure generating grooves and each of the second dynamic pressure generating grooves have an equiangular spiral shape.

Optionally, the hydrodynamic bearings on both chamber walls are arranged in mirror symmetry.

Optionally, the end portions of one ends of the second dynamic pressure grooves, which are far away from the central axis of the liquid inlet, are all located on a fourth circle, and the radius of the fourth circle is equal to the radius of the second circle.

Alternatively, an end portion of one end of the plurality of first dynamic pressure grooves which is close to the center axis of the liquid inlet equally divides the first circle, an end portion of one end of the plurality of first dynamic pressure grooves which is far from the center axis of the liquid inlet equally divides the second circle, and an end portion of one end of the plurality of second dynamic pressure grooves which is close to the center axis of the liquid inlet equally divides the third circle.

Alternatively, in each of the hydrodynamic bearings, the second dynamic pressure groove is provided between every adjacent two of the first dynamic pressure grooves.

Alternatively, the width of the first dynamic pressure groove and the width of the second dynamic pressure groove both gradually increase from one end close to the central axis of the liquid inlet to one end distant from the central axis of the liquid inlet.

Optionally, one end of the first dynamic pressure groove close to the central axis of the liquid inlet and one end of the second dynamic pressure groove far from the central axis of the liquid inlet are both provided with chamfers, and/or one end of the second dynamic pressure groove close to the central axis of the liquid inlet and one end of the second dynamic pressure groove far from the central axis of the liquid inlet are both provided with chamfers.

The inventor researches and discovers that: the impeller of the traditional magnetic suspension pump is easy to collide with the cavity wall because the impeller can incline in the rotating process, and the hydraulic thrust of the hydraulic bearing of the traditional magnetic suspension pump to the periphery of the impeller is insufficient, so that the periphery of the impeller can collide and rub with the cavity wall to cause the abrasion of the impeller.

When the pump body works, external fluid media enter a cavity in the pump shell from a liquid inlet formed in the pump shell and are output from the cavity through centrifugal force generated when the impeller rotates. Because the two opposite cavity walls of the cavity are both provided with the hydrodynamic bearings, each hydrodynamic bearing is provided with a plurality of first dynamic pressure grooves and second dynamic pressure grooves which are alternately arranged at intervals around the central axis of the liquid inlet, the end parts of the ends of the first dynamic pressure grooves, which are close to the central axis of the liquid inlet, are all positioned on a first circle, the end parts of the ends of the first dynamic pressure grooves, which are far away from the central axis of the liquid inlet, are all positioned on a second circle, the end parts of the second dynamic pressure grooves, which are close to the central axis of the liquid inlet, are all positioned on a third circle, the centers of the first circle, the second circle and the third circle are all positioned on the central axis of the liquid inlet, and the radius of the third circle is larger than that of the first circle and smaller than that of the second circle, therefore, the hydrodynamic bearing formed by the combination of the structural characteristics and the arrangement form of the first dynamic pressure grooves and the second dynamic pressure grooves can enable the whole hydraulic thrust to deviate towards the periphery of the, make hydraulic thrust mainly concentrate on the periphery, the hydraulic pressure that is close to impeller central point and puts is less to make and take place the slope at the impeller, above-mentioned hydraulic bearing can produce a very big reverse thrust, pushes the impeller to balanced position fast, with avoid or reduce impeller and chamber wall and bump, thereby the impeller wear rate that makes the pump body is lower and the use reliability is higher.

In a second aspect: providing a pump body, comprising a pump shell and an impeller, wherein a cavity is formed in the pump shell, a liquid inlet communicated with the cavity is further formed in the pump shell, the cavity is provided with two opposite cavity walls on the central axis of the liquid inlet, the impeller can be suspended and rotated in the cavity, the impeller can generate centrifugal force for conveying fluid medium when rotating, the impeller is provided with a first side and a second side which are respectively opposite to the two cavity walls, a hydrodynamic bearing is respectively formed on the first side and the second side, the hydrodynamic bearing is provided with a plurality of first dynamic pressure grooves and a plurality of second dynamic pressure grooves, the plurality of first dynamic pressure grooves and the plurality of second dynamic pressure grooves of the hydrodynamic bearing are alternately arranged around the rotating axis of the impeller at intervals, the length of the first dynamic pressure grooves is greater than that of the second dynamic pressure grooves, and the end parts of the plurality of first dynamic pressure grooves, which are close to one end of the rotating axis of the impeller, are all positioned on a first circle, the end part of one end of the first dynamic pressure groove far away from the rotation axis of the impeller and the end part of one end of the second dynamic pressure groove far away from the rotation axis of the impeller are both positioned on a second circle, the first circle and the second circle are concentric, and the circle center is positioned on the rotation axis of the impeller.

The pump body comprises a pump shell and an impeller, and when the pump body works, an external fluid medium enters a cavity in the pump shell from a liquid inlet formed in the pump shell and is output from the cavity through centrifugal force generated when the impeller rotates. The first side and the second side of the impeller are both provided with a hydrodynamic bearing, the hydrodynamic bearing is provided with a plurality of first dynamic pressure grooves and second dynamic pressure grooves which are alternately arranged at intervals around the rotation axis of the impeller, the end parts of the ends of the first dynamic pressure grooves, which are close to the rotation axis of the impeller, are all positioned on a first circle, the end parts of the ends of the first dynamic pressure grooves, which are far away from the rotation axis of the impeller, and the end parts of the ends of the second dynamic pressure grooves, which are far away from the rotation axis of the impeller, are all positioned on a second circle, the first circle and the second circle are concentric, the circle center is positioned on the rotation axis of the impeller and is smaller than the radius of the second circle, so that the hydrodynamic bearing formed by combining the structural characteristics and the arrangement form of the first dynamic pressure grooves and the second dynamic pressure grooves can enable the whole hydraulic thrust to deviate towards the periphery of the impeller, the hydraulic thrust is mainly, therefore, when the impeller inclines, the hydraulic bearing can generate a large reverse thrust to quickly push the impeller to a balance position so as to avoid or reduce collision between the impeller and the cavity wall, so that the impeller of the pump body has low wear rate and high use reliability.

In a third aspect: a ventricular assist system is provided that includes a blood pump that includes either of the two pump bodies described above.

The ventricle auxiliary system comprises any one of the two pump bodies, and the pump body can obviously reduce the probability of rubbing the impeller of the pump body with the cavity wall of the cavity through the hydraulic bearing with the structure, so that the use reliability of the blood pump comprising the pump body is obviously improved, and the integral working reliability of the ventricle auxiliary system is also improved.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.

FIG. 1 is a cut-away view of an embodiment of a pump body;

fig. 2 is a schematic view of a hydrodynamic bearing of the pump body shown in fig. 1.

Wherein, in the figures, the respective reference numerals:

10-pump shell 11-chamber 12-liquid inlet

13-liquid outlet 14-first dynamic pressure groove 15-second dynamic pressure groove

16-hydrodynamic bearing 17-first circle 18-second circle

19-third circle 20-impeller 11 a-chamber wall

11 b-side wall.

Detailed Description

Reference will now be made in detail to the embodiments of the present application, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to fig. 1 and 2 are exemplary and intended to be used to illustrate the present application and should not be construed as limiting the present application.

In the description of the present application, it is to be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like, as used herein, refer to an orientation or positional relationship indicated in the drawings, which is for convenience and simplicity of description, and does not indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and thus, is not to be considered as limiting.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present application, "a plurality" means two or more unless specifically limited otherwise.

In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

As shown in fig. 1-2, the pump body according to an embodiment can be used in any situation requiring the use of a pump body, and particularly, a non-contact type pump body, such as a magnetic levitation pump, can be used as a blood pump of a ventricular assist system.

The pump body includes pump case 10 and impeller 20, is formed with cavity 11 in the pump case 10, and still seted up liquid inlet 12 and the liquid outlet 13 that is linked together with cavity 11 on the pump case 10. The chamber 11 has two chamber walls 11a disposed opposite to each other, and the liquid inlet 12 is opened in one of the chamber walls 11 a. The chamber 11 also has a side wall 11b connecting the two chamber walls 11a, and the liquid outlet 13 is located at the side wall 11 b.

The impeller 20 can be suspended and rotated in the chamber 11, and the impeller 20 can generate a centrifugal force for conveying the fluid medium, so that the fluid medium can enter the chamber 11 from the liquid inlet 12 and be output from the liquid outlet 13. In theory, if the impeller 20 does not tilt during rotation, the axis of rotation of the impeller 20 is parallel to or coincides with the central axis of the inlet 12. Specifically, the impeller 20 is capable of levitating rotation under the influence of magnetic force. Here, the levitation rotation of the impeller 20 means that the impeller 20 does not contact the cavity wall 11a of the chamber 11 while rotating.

The chamber 11 is formed with hydrodynamic bearings 16 on two opposite chamber walls 11a on the central axis of the liquid inlet 13, the hydrodynamic bearings 16 have a plurality of first dynamic pressure grooves 14 and a plurality of second dynamic pressure grooves 15, and the plurality of first dynamic pressure grooves 14 and the plurality of second dynamic pressure grooves 15 are alternately arranged at intervals around the central axis of the liquid inlet 12. The length of the first dynamic pressure groove 14 is greater than that of the second dynamic pressure groove 15, the end portions of the ends, close to the central axis of the liquid inlet 12, of the first dynamic pressure grooves 14 are all located on a first circle 17, the end portions, far away from the central axis of the liquid inlet 12, of the first dynamic pressure grooves 14 are all located on a second circle 18, the end portions, close to the central axis of the liquid inlet 12, of the second dynamic pressure grooves 15 are all located on a third circle 19, the centers of the first circle 17, the second circle 18 and the third circle 19 are all located on the central axis of the liquid inlet 12, and the radius of the third circle 19 is greater than that of the first circle 17 and smaller than that of the second circle 18.

The inventor researches and discovers that: the impeller of the conventional magnetic suspension pump is easy to collide with the chamber wall because the impeller can incline in the rotating process, and the hydraulic thrust of the hydraulic bearing of the conventional magnetic suspension pump to the periphery of the impeller 20 is insufficient, so that the periphery of the impeller 20 can collide and rub with the chamber wall to cause the abrasion of the impeller 20.

The pump body of the present application includes a pump casing 10 and an impeller 20, and when the pump body works, an external fluid medium enters a chamber 11 in the pump casing 10 from a liquid inlet 12 formed in the pump casing 10, and is output from a liquid outlet 13 by a centrifugal force generated when the impeller 20 rotates. Because the two cavity walls 11a are both formed with the hydrodynamic bearing 16, the hydrodynamic bearing 16 has a plurality of first dynamic pressure grooves 14 and second dynamic pressure grooves 15 alternately arranged around the central axis of the liquid inlet 12 at intervals, the end portions of the ends of the first dynamic pressure grooves 14 close to the central axis of the liquid inlet 12 are all located on the first circle 17, the end portions of the ends of the first dynamic pressure grooves 14 far away from the central axis of the liquid inlet 12 are all located on the second circle 18, the end portions of the second dynamic pressure grooves 15 close to the end of the central axis of the liquid inlet 12 are all located on the third circle 19, the centers of the first circle 17, the second circle 18 and the third circle 19 are all located on the central axis of the liquid inlet 12, and the radius of the third circle 19 is greater than the radius of the first circle 17 and smaller than the radius of the second circle 18. Thus, the hydrodynamic bearing 16 formed by combining the above structural features and arrangement of the first dynamic pressure groove 14 and the second dynamic pressure groove 15 can shift the entire hydraulic thrust to the periphery of the impeller 20, so that the hydraulic thrust is mainly concentrated on the periphery, and the hydraulic pressure near the center of the impeller 20 is small, so that the impeller 20 is inclined, and the hydrodynamic bearing can generate a large reverse thrust to push the impeller 20 to a balance position quickly, so as to avoid or reduce collision between the impeller 20 and the cavity wall 11a, so that the impeller of the pump body has a low wear rate and high use reliability.

In one of the embodiments, as shown in fig. 2, each of the first dynamic pressure grooves 14 and each of the second dynamic pressure grooves 15 has an equiangular spiral shape. Specifically, by arranging each first dynamic pressure groove 14 and each second dynamic pressure groove 15 in an equiangular spiral line shape, a thrust away from the cavity wall 11a is provided to the impeller 20 in this way, and the impeller 20 is pushed in a direction away from the cavity wall 11a, so that the impeller 20 and the cavity wall 11a are prevented from being rubbed.

In one embodiment, as shown in fig. 2, the hydrodynamic bearings 16 on the two chamber walls 11a are arranged in mirror symmetry. Specifically, through making hydrodynamic bearing 16 on two chamber walls 11a be mirror symmetry and setting, guaranteed just so that impeller 20 corresponds two chamber walls 11a and just can exert the same driving force to the both sides wall of impeller 20 that corresponds to make impeller 20 when rotating, even its rotation gesture or position take place the skew, also can reply to the correct position fast under the same driving force effect in both sides for impeller 20 can maintain good dynamic stability.

In one embodiment, as shown in fig. 2, the ends of the second dynamic pressure grooves 15 at the ends away from the central axis of the liquid inlet 12 are all located on a fourth circle, the radius of which is equal to the radius of the second circle 18. Specifically, by making the ends of the plurality of second dynamic pressure grooves 15, which are away from the central axis of the liquid inlet 12, all lie on a fourth circle having a radius equal to that of the second circle 18, the hydrodynamic bearing 16 is further enabled to quickly push the impeller 20 to the equilibrium position to avoid or reduce collision of the impeller 20 with the chamber wall 11 a.

In one of the embodiments, as shown in fig. 2, the end portion of one end of the plurality of first dynamic pressure grooves 14 close to the central axis of the liquid inlet 12 bisects a first circle 17, the end portion of one end of the plurality of first dynamic pressure grooves 14 far from the central axis of the liquid inlet 12 bisects a second circle 18, and the end portion of one end of the plurality of second dynamic pressure grooves 15 far from the central axis of the liquid inlet 12 bisects a third circle 19.

Specifically, by dividing the two ends of each first dynamic pressure groove 14 into the first circle 17 and the second circle 18 equally, the fluid medium can be further guided and guided to the outer periphery of the impeller 20 uniformly, and the magnitude of the hydraulic thrust applied by the fluid medium to all positions of the outer periphery of the impeller 20 can be made to be consistent. By making both ends of each second dynamic pressure groove 15 equally divide the first circle 17 and the third circle 19, the consistency of the magnitude of the hydraulic thrust applied by the fluid medium to all over the outer periphery of the impeller 20 is further improved.

Specifically, in the illustrated embodiment, the ends of the plurality of first dynamic pressure grooves 14 and the plurality of second dynamic pressure grooves 15, which are away from the central axis of the liquid inlet 12, commonly bisect the second circle 18.

In one embodiment, as shown in fig. 2, in each hydrodynamic bearing 16, a second dynamic pressure groove 15 is provided between each adjacent two first dynamic pressure grooves 14. Specifically, in the present embodiment, when the first dynamic pressure grooves 14 and the second dynamic pressure grooves 15 are alternately arranged, one second dynamic pressure groove 15 may be formed between two adjacent first dynamic pressure grooves 14, that is, one first dynamic pressure groove 14 and one second dynamic pressure groove 15 are alternately arranged. It should be noted that the alternating arrangement of the first dynamic pressure grooves 14 and the second dynamic pressure grooves 15 is not limited to the above-mentioned manner, and two or more second dynamic pressure grooves 15 may be formed between two adjacent first dynamic pressure grooves 14, that is, a plurality of second dynamic pressure grooves 15 are formed between two adjacent first dynamic pressure grooves 14.

In one embodiment, as shown in fig. 2, the width of the first dynamic pressure groove 14 and the width of the second dynamic pressure groove 15 are gradually increased from the end close to the central axis of the liquid inlet 12 to the end far from the central axis of the liquid inlet 12, so that more fluid medium is guided to the outer periphery of the impeller 20, thereby increasing the amount of hydraulic thrust applied by the fluid medium to all over the outer periphery of the impeller 20.

Alternatively, the first dynamic pressure grooves 14 and the second dynamic pressure grooves 15 are the same in depth. This can ensure the flow balance when the fluid medium is guided to the outer periphery of the impeller 20 by the first dynamic pressure groove 14 and the second dynamic pressure groove 15, so that the magnitude of the hydraulic thrust applied by the fluid medium to all positions of the outer periphery of the impeller 20 tends to be consistent.

In one embodiment, the first dynamic pressure groove 14 is chamfered at both the end close to the central axis of the liquid inlet 12 and the end far from the central axis of the liquid inlet 12, which can reduce the occurrence of hemolysis.

In one embodiment, the second dynamic pressure groove 15 is chamfered at both the end close to the central axis of the liquid inlet 12 and the end far from the central axis of the liquid inlet 12 to reduce the occurrence of hemolysis.

Alternatively, the arc design of the first dynamic pressure groove 14 and the second dynamic pressure groove 15 satisfies the following logarithmic spiral formula:

ρ＝αe^kφ；

where ρ represents the pole diameters of the first dynamic pressure groove 14 and the second dynamic pressure groove 15, Φ is the pole angle of the first dynamic pressure groove 14 and the second dynamic pressure groove 15, and α and k are both constants.

The present application also provides another embodiment of a pump body having substantially the same structure as the pump body of the embodiment shown in fig. 1 and 2, except that in this embodiment the hydrodynamic bearing is provided not on the chamber wall of the chamber, but on the impeller.

That is, the pump body of the present embodiment also includes a pump casing and an impeller, a cavity is formed in the pump casing, a fluid inlet communicated with the cavity is further formed in the pump casing, the cavity has two opposite cavity walls on a central axis of the fluid inlet, the impeller can be suspended and rotated in the cavity, a centrifugal force for conveying a fluid medium can be generated when the impeller is rotated, and the impeller has a first side and a second side which are opposite to the two cavity walls respectively.

The difference is that the first side and the second side of the impeller of the present embodiment are both formed with hydrodynamic bearings, each hydrodynamic bearing has a plurality of first dynamic pressure grooves and a plurality of second dynamic pressure grooves, the plurality of first dynamic pressure grooves and the plurality of second dynamic pressure grooves of the hydrodynamic bearing are alternately arranged at intervals around the rotation axis of the impeller, the length of the first dynamic pressure grooves is longer than that of the second dynamic pressure grooves, and the ends of the plurality of first dynamic pressure grooves close to the rotation axis of the impeller are all located on a first circle, the ends of the plurality of first dynamic pressure grooves far from the rotation axis of the impeller and the ends of the plurality of second dynamic pressure grooves far from the rotation axis of the impeller are all located on a second circle, and the first circle and the second circle are concentric, and the center of the circle is located on the rotation axis of the impeller. In the present embodiment, the first dynamic pressure groove and the second dynamic pressure groove are different in configuration and the like from the previous embodiment except for the arrangement position.

When the pump body works, an external fluid medium enters a cavity in the pump shell from a liquid inlet formed in the pump shell and is output from the cavity through centrifugal force generated when the impeller rotates. The first side and the second side of the impeller are both provided with a hydrodynamic bearing, the hydrodynamic bearing is provided with a plurality of first dynamic pressure grooves and second dynamic pressure grooves which are alternately arranged at intervals around the rotation axis of the impeller, the end parts of the ends of the first dynamic pressure grooves, which are close to the rotation axis of the impeller, are all positioned on a first circle, the end parts of the ends of the first dynamic pressure grooves, which are far away from the rotation axis of the impeller, and the end parts of the ends of the second dynamic pressure grooves, which are far away from the rotation axis of the impeller, are all positioned on a second circle, the first circle and the second circle are concentric, the circle center is positioned on the rotation axis of the impeller and is smaller than the radius of the second circle, so that the hydrodynamic bearing formed by combining the structural characteristics and the arrangement form of the first dynamic pressure grooves and the second dynamic pressure grooves can enable the whole hydraulic thrust to deviate towards the periphery of the impeller, the hydraulic thrust is mainly, therefore, when the impeller inclines, the hydraulic bearing can generate a large reverse thrust to quickly push the impeller to a balance position so as to avoid or reduce collision between the impeller and the cavity wall, so that the impeller of the pump body has low wear rate and high use reliability.

The embodiment of the application also provides a ventricular assist system, which comprises a blood pump, wherein the blood pump comprises any one of the two pump bodies.

According to the ventricle auxiliary system provided by the embodiment of the application, the blood pump arranged in the ventricle auxiliary system comprises any one of the two pump bodies, the pump body is provided with the first dynamic pressure groove 14 and the second dynamic pressure groove 15, and the probability of rubbing the impeller 20 of the pump body with the cavity wall of the cavity 11 is remarkably reduced through the combination of the structural characteristics and the arrangement form of the first dynamic pressure groove 14 and the second dynamic pressure groove 15, so that the use reliability of the blood pump comprising the pump body is remarkably improved, and the integral working reliability of the ventricle auxiliary system is also improved.

The present invention is not intended to be limited to the particular embodiments shown and described, but is to be accorded the widest scope consistent with the principles and novel features herein disclosed.