CN109538468B

CN109538468B - Double-acting variable vane pump

Info

Publication number: CN109538468B
Application number: CN201811142374.1A
Authority: CN
Inventors: 陈行
Original assignee: Zhejiang University ZJU
Current assignee: Zhejiang University ZJU
Priority date: 2018-09-28
Filing date: 2018-09-28
Publication date: 2020-02-18
Anticipated expiration: 2038-09-28
Also published as: CN109538468A

Abstract

The invention discloses a double-acting variable vane pump, which comprises a shell, a rotor and vanes, wherein the rotor is positioned in the center, the shell covers the outside of the rotor, a circle of circular ring K1 extends towards the direction of the center of a sphere from the center of the inner wall of the shell, the inner wall of the shell is uniformly provided with at least three left positioning grooves and at least three right positioning grooves along the circumferential direction, and the vanes are arranged on the left positioning grooves and the right positioning grooves; a ring groove is formed in the centering position of the side wall of the rotor, a left sliding groove is formed in the left side face of the ring groove, a right sliding groove is formed in the right side face of the ring groove, and a blade on the left positioning groove is further arranged on the left sliding groove in a sliding mode; the blade on the right positioning groove is also arranged on the right sliding groove in a sliding manner; the ring K1 is clamped between the vanes on the left positioning groove and the vanes on the right positioning groove, and a containing cavity is formed between every two adjacent vanes, the surface of the ring groove, the inner wall of the shell and the side wall of the ring K1; the axis of the rotor and the axis of the housing do not coincide; the relative linear velocity of the blade and the shell is zero, and the blade can run at extremely high speed.

Description

Double-acting variable vane pump

Technical Field

The invention relates to a multi-vane pump, in particular to a double-acting variable vane pump.

Background

The existing vane pump structure is that a rotor is eccentrically arranged in an oil cylinder body, vanes are radially arranged in the rotor or form a certain angle with the radius of the rotor, the rotor rotates at a high speed when in work, the vanes are thrown out under the action of centrifugal force to form a sealed cavity with the oil cylinder body, and the volume changes to generate pressure when the vanes rotate. . The vane pump has the advantages that the sealing performance is poor and the output pressure is low because the vanes and the oil cylinder body are sealed by a contact line, and in addition, the relative linear velocity of the vanes and the oil cylinder body is very high during rotation, so that great friction is generated, the whole vane pump is quickly abraded, the service life is short, and the efficiency is low. Thus, the rotational speed of the pump cannot be too high. In addition, in order to ensure that the vanes can be safely moved in and out of the rotor during rotation, the rotor must have a considerable diameter, which necessitates a small displacement, particularly in variable displacement pumps.

Disclosure of Invention

The invention aims to provide a double-acting variable vane pump which has the advantages that all sealing parts are surface seals, the pump is not easy to wear, the relative linear velocity of a vane and a shell is zero, the pump can run at extremely high speed, the pump has small volume and large discharge capacity, and the output pressure is high.

In order to achieve the purpose, the technical scheme adopted by the invention is as follows: a double-acting variable vane pump comprises a shell, a rotor, vanes, an oil distribution block and a guide block, wherein the rotor is positioned in the center, the shell covers the outside of the rotor, a circle of circular ring K1 extends towards the direction of the center of a sphere at the centering position of the inner wall of the shell, at least three left positioning grooves are uniformly formed in the inner wall of the shell along the circumferential direction, right positioning grooves which are in one-to-one correspondence with the left positioning grooves are uniformly formed in the inner wall of the shell along the circumferential direction, the left positioning grooves and the right positioning grooves are symmetrically arranged relative to the circular ring K1, and the vanes are arranged on; the centering part of the side wall of the rotor is provided with an annular groove, the left side surface of the annular groove is provided with left sliding chutes which are in one-to-one correspondence with the left positioning grooves, the right side surface of the annular groove is provided with right sliding chutes which are in one-to-one correspondence with the right positioning grooves, and blades on the left positioning grooves are also arranged on the left sliding chutes in a sliding manner and are sealed through sealing elements; the blade on the right positioning groove is also arranged on the right sliding groove in a sliding manner and is sealed by a sealing element; the ring K1 is clamped between the blade on the left positioning groove and the blade on the right positioning groove, a containing cavity is formed between two adjacent blades, the surface of the ring groove, the inner wall of the shell and the side wall of the ring K1, oil ports with the same number as the containing cavities are formed in the rotor, one oil port is communicated with one containing cavity, and the two ends of the rotor are connected with oil distribution blocks; the outer wall of the shell is provided with a convex circular ring J1, and the convex circular ring J1 is placed in the guide groove of the guide block; the axis of the rotor and the axis of the housing do not coincide;

when the rotor rotates, the rotor drives the blades to rotate together, in the rotating process, the blades on the left sliding groove and the right sliding groove periodically complete telescopic movement, so that the volume of the containing cavity is periodically changed, a high-pressure containing cavity and a low-pressure containing cavity are periodically formed, the low-pressure containing cavity absorbs oil through the oil distribution block, and the high-pressure containing cavity discharges oil through the oil distribution block.

Furthermore, a waist drum-shaped ball table A2 with two parallel truncated spherical crowns at two ends is arranged in the rotor, a conical side surface C2 and a conical side surface D2 are arranged at two ends of the ball table A2, and a ring groove is formed by the ball table A2, the conical side surface C2 and the conical side surface D2; the conical side surface C2 is provided with grooves E2 which are in one-to-one correspondence with the right positioning grooves, the grooves E2 are evenly divided into the conical side surface C2, and the grooves E2 are right sliding grooves; the conical side surface D2 is provided with grooves F2 which correspond to the left positioning grooves one by one, the conical side surface D2 is equally divided, and the groove F2 is a left sliding groove; a hole K2 is formed between two adjacent grooves E2 on the conical side surface C2, a hole K2 ' is formed between two adjacent grooves F2 on the conical side surface D2, the surface connected with the conical side surface C2 is a spherical surface G2, the surface connected with the conical side surface D2 is a spherical surface H2, the radiuses and the spherical centers of the spherical surfaces G2 and H2 are the same as those of the spherical surface A1 in the shell, the two end surfaces of the rotor are a circular ring surface I2 and a circular ring surface J2, holes L2 corresponding to the hole K2 are uniformly distributed on the circular ring surface I2, holes L2 ' corresponding to the holes K2 ' are uniformly distributed on the circular ring surface J2, and the holes L2 are communicated with the holes K2 corresponding to the holes to form a second oil port for oil inlet or oil discharge; the hole L2 ' is communicated with the hole K2 ' corresponding to the hole L2 ' to form a first oil port for oil feeding or oil discharging.

Furthermore, the cross sections of the groove E2 and the groove F2 are formed by sequentially connecting a conical plane S2, an arc P2 and a conical plane M2, the outer ends of the conical plane S2 and the conical plane M2 are connected with an arc R2, the two arcs R2 are concentric, and a sealing element is arranged in each arc R2.

Furthermore, the sealing element comprises cushion blocks and elastic sealing strips, one elastic sealing strip and one cushion block are sequentially arranged on each circular arc R2 from inside to outside, and the two cushion blocks are respectively positioned at two sides of one blade and are abutted against the blade;

alternatively, the pad and the flexible seal strip may be combined to be integrally placed in the circular arc R2.

Furthermore, the cushion block is in a long strip shape, the cross section of the cushion block is in a crescent shape, and the length of the cushion block is equal to the radial length of the ring K1;

the elastic sealing strip is strip-shaped, the cross section of the elastic sealing strip is semicircular, the radius of an outer circle of the elastic sealing strip is the same as that of the circular arc R2, the radius of an inner circle of the elastic sealing strip is the same as that of the crescent of the cushion block, and the length of the elastic sealing strip is equal to that of the circular ring K1 in the radial direction.

Furthermore, the shell is provided with an inner spherical surface A1 and an outer spherical surface B1, the inner spherical surface A1 and the outer spherical surface B1 are waist drum-shaped spherical surfaces with two ends parallelly cut off spherical crowns with the same size, a circle of circular ring K1 extends towards the center of the sphere from the middle of the inner spherical surface A1, two parallel circular ring planes C1 and D1 are arranged on two sides of the circular ring K1, and the middle of the circular ring K1 is provided with the inner spherical surface E1, the diameter of which is equal to that of the spherical table A2; at least three grooves P1 are uniformly arranged on the inner wall of the shell along the circumferential direction, namely left positioning grooves; the inner wall of the shell is uniformly provided with grooves P1 ' which are in one-to-one correspondence with the left positioning grooves along the circumferential direction, namely the right positioning grooves, the grooves P1 and the grooves P1 ' are symmetrically arranged about the circular ring K1, the widths of the grooves P1 and the grooves P1 ' are the same as the thickness of the blades, and the middle part of the outer spherical surface B1 protrudes outwards for a circle of circular ring J1.

Furthermore, the blade is formed by enclosing a front parallel plane A3, a rear parallel plane B3, an upper cylindrical surface C3, a lower cylindrical surface D3, and a side surface and a long cylindrical surface F3 on the other side; the radius and the center of the cylindrical surface C3 are respectively the same as those of the groove bottom surface of the groove P1 or the groove P1' on the shell, and the radius and the center of the cylindrical surface D3 are respectively the same as those of the ball table A2; the long cylindrical surface F3 is hinged on the slipper.

Furthermore, the oil distribution block is a cylinder, the diameter of the outer cylindrical surface A4 of the cylinder is equal to the diameters of the circular surfaces I2 and J2 at the two ends of the rotor, two kidney-shaped through holes B4 and C4 are formed in the cylinder, one kidney-shaped through hole is communicated with the high-pressure cavity, and the other kidney-shaped through hole is communicated with the low-pressure cavity.

Further, the outer end of the blade is mounted on a slipper which abuts against the side surface of the ring K1.

Furthermore, the sliding shoe is in a long strip shape and is formed by enclosing a left parallel plane A5, a right parallel plane B5, an upper spherical surface C5, a lower spherical surface D5, a bottom surface E5 and a concave cylindrical surface F5 on the other side; the radius and the circle center of the outer spherical surface C5 are the same as those of the spherical surface A1 in the shell, the radius and the circle center of the lower spherical surface D5 are the same as those of the rotor spherical surface A2, and the radius and the circle center of the concave cylindrical surface F5 are the same as those of the blade long cylindrical surface F3; the bottom surface E5 abuts on the annular flat surface C1 or the annular flat surface D1 of the annular ring K1.

The invention has the advantages that:

1) all sealing parts are surface sealing;

2) the discharge capacity is large, the pressure is high, and the efficiency is high;

3) compared with the traditional plunger pump and the traditional vane pump, the vane pump provided by the invention has high specific power;

4) the flow of the pump can be adjusted by adjusting the inclination angle of the guide block, namely adjusting the included angle between the axis of the ring K1 in the shell and the axis of the rotor;

5) the relative linear velocity of the rotor and the shell is very low, and the rotor can run at extremely high speed;

6) the structure is compact, and the processing is relatively easy;

7) low cost and long service life.

8) The double-acting form is adopted, and compared with the single-acting form, the specific power is larger.

Drawings

The invention is further illustrated by the following figures and examples.

FIG. 1 is a schematic view of the overall structure of the present invention;

FIG. 2a is a schematic view of the housing construction of the present invention;

FIG. 2b is a schematic view of the kk section of FIG. 2 a;

FIG. 3a is a schematic view of a rotor construction;

FIG. 3b is a left side view of FIG. 3 a;

FIG. 3c is a schematic cross-sectional view T-T of FIG. 3 a;

FIG. 4a is a schematic view of a blade configuration of the present invention;

FIG. 4b is a view from direction K of FIG. 4 a;

FIG. 5 is a schematic view of the oil distribution block structure of the present invention;

FIG. 6a is a schematic view of a slipper of the present invention;

FIG. 6b is a schematic cross-sectional view of the MM of FIG. 6 a;

FIG. 7 is a schematic view of a blade and slipper configuration of the present invention;

FIG. 8 is a longitudinal schematic view of the spacer of the present invention;

FIG. 9 is a longitudinal schematic view of the flexible sealing strip of the present invention;

FIG. 10 is a partial schematic view of a rotor, blades, spacer blocks and elastomeric seal strips of the present invention;

FIG. 11 is a schematic view of the eccentric placement of the spacer and resilient seal in grooves E2 and F2;

in the figure: 1. the novel oil distribution structure comprises a shell, 2 parts of a rotor, 3 parts of blades, 4 parts of oil distribution blocks, 5 parts of sliding shoes, 6 parts of guide blocks, 7 parts of cushion blocks and 8 parts of elastic sealing strips.

Detailed Description

Reference will now be made in detail to the exemplary embodiments, examples of which are illustrated in the accompanying drawings. In the following description and in the drawings, the same numbers in different drawings identify the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present invention. Rather, they are merely examples of apparatus consistent with certain aspects of the invention, as detailed in the claims below. Various embodiments of the present description are described in an incremental manner.

It should be noted that all the directional indicators (such as up, down, left, right, front, and rear … …) in the embodiment of the present invention are only used to explain the relative position relationship between the components, the movement situation, etc. in a specific posture (as shown in the drawing), and if the specific posture is changed, the directional indicator is changed accordingly.

In addition, the descriptions related to "first", "second", etc. in the present invention are 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 at least one such feature. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.

As shown in fig. 1, an embodiment of the present invention provides a double-acting variable vane pump, including a casing 1, a rotor 2, vanes 3, an oil distribution block 4, and a guide block 6, where the rotor 2 is located at the center, the casing 1 covers the outside of the rotor 2, a circle of ring K1 extends from the center of the inner wall of the casing 1 to the direction of the sphere center, the inner wall of the casing 1 is uniformly provided with at least three left positioning grooves along the circumferential direction, the inner wall of the casing 1 is uniformly provided with right positioning grooves corresponding to the left positioning grooves one by one along the circumferential direction, the left positioning grooves and the right positioning grooves are symmetrically arranged with respect to the ring K1, and the vanes 3 are mounted on the left positioning; a ring groove is formed in the side wall of the rotor 2 at the middle position, left sliding grooves which are in one-to-one correspondence with the left positioning grooves are formed in the left side face of the ring groove, right sliding grooves which are in one-to-one correspondence with the right positioning grooves are formed in the right side face of the ring groove, and the blades 3 on the left positioning grooves are further arranged on the left sliding grooves in a sliding mode and sealed through sealing elements; the blade 3 on the right positioning groove is also arranged on the right sliding groove in a sliding manner and is sealed by a sealing element; the ring K1 is clamped between the blade 3 on the left positioning groove and the blade 3 on the right positioning groove, a containing cavity is formed between two adjacent blades 3, the surface of the ring groove, the inner wall of the shell 1 and the side wall of the ring K1, oil ports with the same number as the containing cavities are formed in the rotor 2, one oil port is communicated with one containing cavity, and the two ends of the rotor 2 are both connected with oil distribution blocks 4; the outer wall of the shell 1 is provided with a convex circular ring J1, and the convex circular ring J1 is arranged in the guide groove of the guide block 6; the axis of the rotor 2 and the axis of the housing 1 do not coincide;

when rotor 2 rotates, rotor 2 drives blade 3 and rotates together, and at the rotation in-process, blade 3 periodic completion concertina movement on left spout and the right spout for the volume that holds the chamber takes place periodic change, and then periodic formation high pressure holds the chamber and holds the chamber with low pressure, and the low pressure holds the chamber and passes through the oil absorption of oil distribution block 4, and the high pressure holds the chamber and passes through the oil extraction of oil distribution block 4.

It should be noted that the number of the blades 3 is at least 6, the number of the sliding grooves (left sliding groove and right sliding groove) and the number of the sliding shoes are all the same as the number of the blades 3, and the number of the blades 3 is taken as 18 as an example to further illustrate the specific solution of the present invention, and those skilled in the art can also obtain other embodiments without any doubt from the following description.

Fig. 2a and 2b are schematic diagrams of the shape and structure of the housing 1 of the present invention. The shell 1 is provided with an inner spherical surface A1 and an outer spherical surface B1, the inner spherical surface A1 and the outer spherical surface B1 are waist drum-shaped spherical surfaces with two ends parallelly cut off spherical crowns with the same size, a circle of circular ring K1 extends towards the center of the sphere from the middle of the inner spherical surface A1, two parallel circular ring planes C1 and D1 are arranged on two sides of the circular ring K1, the middle of the circular ring K1 is provided with the inner spherical surface E1, and the diameter of the inner spherical surface E1 is equal to that of the ball table A2; nine grooves P1 are uniformly formed in the inner wall of the shell 1 along the circumferential direction, namely left positioning grooves; the inner wall of the shell 1 is uniformly provided with grooves P1 ' which are in one-to-one correspondence with the left positioning grooves along the circumferential direction, namely the right positioning grooves, the grooves P1 and the grooves P1 ' are symmetrically arranged relative to a circular ring K1, the widths of the grooves P1 and the grooves P1 ' are the same as the thickness of the blades 3, and the middle part of an outer spherical surface B1 protrudes outwards for a circle of circular ring J1; the thickness of the ring J1 is the same as that of the ring K1, which is similar to the outward extension part of the ring K1, the ring K1 and the ring J1 form a large ring, the large ring can be separated from the shell 1 to form a swash plate, and the left half and the right half of the original shell 1 are tightly fixed on the swash plate.

Fig. 3a and 3b are schematic views showing the shape and structure of the rotor 2 of the present invention. The rotor 2 is a waist drum-shaped ball table A2 with two ends cutting off two ball crowns in parallel, two ends of the ball table A2 are a conical side surface C2 and a conical side surface D2, and the ball table A2, the conical side surface C2 and the conical side surface D2 form a ring groove; the conical side surface C2 is provided with grooves E2 which are in one-to-one correspondence with the right positioning grooves, the grooves E2 are evenly divided into the conical side surface C2, and the grooves E2 are right sliding grooves; the conical side surface D2 is provided with grooves F2 which correspond to the left positioning grooves one by one, the conical side surface D2 is equally divided, and the groove F2 is a left sliding groove; a hole K2 is formed between two adjacent grooves E2 on the conical side surface C2, a hole K2 ' is formed between two adjacent grooves F2 on the conical side surface D2, the surface connected with the conical side surface C2 is a spherical surface G2, the surface connected with the conical side surface D2 is a spherical surface H2, the radiuses and the spherical centers of the spherical surfaces G2 and H2 are the same as the radius and the spherical center of the spherical surface A1 in the shell 1, two end surfaces of the rotor 2 are a circular ring surface I2 and a circular ring surface J2, a hole L2 corresponding to the hole K2 is uniformly distributed on the circular ring surface I2, a hole L2 ' corresponding to the hole K2 ' is uniformly distributed on the circular ring surface J2, and the hole L2 is communicated with the hole K2 corresponding to the hole to form a second oil port for oil inlet or oil discharge; the hole L2 ' is communicated with the hole K2 ' corresponding to the hole L2 ' to form a first oil port for oil feeding or oil discharging. As shown in fig. 3c, the cross-sectional shapes of the groove E2 and the groove F2 are all formed by sequentially connecting a conical plane S2, an arc P2 and a conical plane M2, the outer ends of the conical plane S2 and the conical plane M2 are both connected with an arc R2, the two arcs R2 are concentric, and a sealing element is installed in each arc R2.

Fig. 4a and 4b are schematic views of the shape and structure of the blade 3 of the present invention. The blades 3 share 18 same blades, and the blades 3 are enclosed by a front parallel plane A3 and a rear parallel plane B3, an upper cylindrical surface C3 and a lower cylindrical surface D3, and a long cylindrical surface F3 on one side and the other side; the radius and the center of the cylindrical surface C3 are respectively the same as those of the groove bottom surface of the groove P1 or the groove P1' on the shell 1, and the radius and the center of the cylindrical surface D3 are respectively the same as those of the ball table A2; the oblong cylindrical surface F3 is hinged to the slipper 5, as shown in fig. 7.

Fig. 5 is a schematic diagram of the shape and structure of the oil distribution block 4 of the present invention. The oil distribution block 4 is a cylinder, the diameter of the outer cylindrical surface A4 of the cylinder is equal to the diameter of the circular surfaces I2 and J2 at the two ends of the rotor 2, two kidney-shaped through holes B4 and C4 are formed in the cylinder, one kidney-shaped through hole is communicated with the high-pressure cavity, and the other kidney-shaped through hole is communicated with the low-pressure cavity.

Fig. 6a and 6b are schematic views of the shape and structure of the slipper 5 of the present invention. Preferably, the outer end of the blade 3 is mounted on the slipper 5, and the slipper 5 abuts against the side surface of the ring K1; the sliding shoe 5 is in a long strip shape, has 18 same pieces, and is formed by enclosing a left parallel plane A5, a right parallel plane B5, an upper spherical surface C5, a lower spherical surface D5, a bottom surface E5 and a concave cylindrical surface F5 on the other side; the radius and the circle center of the outer spherical surface C5 are the same as those of the inner spherical surface A1 of the shell 1, the radius and the circle center of the lower spherical surface D5 are the same as those of the spherical surface A2 of the rotor 2, and the radius and the circle center of the concave cylindrical surface F5 and the long cylindrical surface F3 of the blade 3 are the same; the bottom surface E5 abuts on the annular flat surface C1 or the annular flat surface D1 of the annular ring K1.

The sealing element comprises cushion blocks 7 and elastic sealing strips 8, one elastic sealing strip 8 and one cushion block 7 are sequentially arranged on each circular arc R2 from inside to outside, and the two cushion blocks 7 are respectively positioned at two sides of one blade 3 and are abutted against the blade 3; alternatively, the pad 7 and the elastic sealing strip 8 can be combined into a whole to be placed in the circular arc R2.

Fig. 8 is a schematic structural diagram of the shape of the spacer 7 of the present invention. The cushion block 7 is long-strip-shaped, the cross section of the cushion block is crescent-shaped, and the length of the cushion block is equal to the radial length of the circular ring K1; the number of the cushion blocks 7 is 36.

Fig. 9 is a schematic view of the shape structure of the elastic weather strip 8 of the present invention. The elastic sealing strip 8 is in a strip shape, the cross section of the elastic sealing strip is in a semicircular ring shape, the radius of the outer circle of the elastic sealing strip is the same as that of the circular arc R2, the radius of the inner circle of the elastic sealing strip is the same as that of the crescent of the cushion block 7, the elastic sealing strip is concentric (as shown in figure 10) or not concentric (as shown in figure 11), and the length of the elastic sealing strip is equal to the radial length of the circular ring K35; the number of the elastic sealing strips 8 is 36.

Other techniques not described are all known to those skilled in the art, and are not described herein again.

The operation principle of the invention is as follows:

a closed cavity is formed among the two adjacent blades 3, the surface of the ring groove, the inner wall of the shell 1 and the side wall of the ring K1, and 18 cavities are formed in total, namely 9 cavities are formed on the left side and 9 cavities are formed on the right side of the ring K1;

taking the right end of the pump as an example, as shown in fig. 1, at the uppermost end, the housing 1 ring K1 is at the leftmost position, where the volume of the chamber is at its maximum. At the lowermost end, where housing 1 ring K1 is at the far right, the volume of the chamber is at its smallest. When the rotor 2 rotates, the rotor 2 drives the blades 3 to rotate together, in the rotating process, the blades 3 on the left sliding groove and the right sliding groove periodically complete telescopic movement, so that the volume of the containing cavity is periodically changed, the volume of the containing cavity at the lowest end of the pump is gradually increased from the minimum, the containing cavity is disconnected with the high-pressure cavity and is communicated with the low-pressure cavity through the oil distribution block 4 at the right end, and the containing cavity starts to absorb oil through the oil distribution block 4 at the right end. The volume of the chamber is maximized when the rotor 2 is rotated from the lowermost end to the uppermost end. When the rotor 2 continues to rotate, namely rotates from the uppermost end to the lowermost end, the volume of the containing cavity begins to shrink, the containing cavity is disconnected from the low-pressure cavity and communicated with the high-pressure cavity through the oil distribution block 4 at the right end, and the containing cavity begins to discharge oil through the oil distribution block 4 at the right end. This completes one cycle. The rotation is continued, and the oil is continuously absorbed and discharged in such a way repeatedly. The other chambers are also the same.

Similarly, at the left end of the pump, the situation is reversed from that at the right end, thereby achieving double action.

The flow rate of the pump can be adjusted by adjusting the inclination angle of the guide block 6, i.e. the angle between the axis of the ring K1 in the housing 1 and the axis of the rotor 2.

The above-described embodiments are intended to illustrate rather than to limit the invention, which is intended to be covered by the following claims.

Claims

1. A double-acting variable vane pump is characterized by comprising a shell (1), a rotor (2), vanes (3), an oil distribution block (4) and a guide block (6), wherein the rotor (2) is positioned in the center, the shell (1) covers the outer part of the rotor (2), a circle of ring K1 extends towards the direction of the center of a sphere at the centering position of the inner wall of the shell (1), at least three left positioning grooves are uniformly formed in the inner wall of the shell (1) along the circumferential direction, right positioning grooves which are in one-to-one correspondence with the left positioning grooves are uniformly formed in the inner wall of the shell (1) along the circumferential direction, the left positioning grooves and the right positioning grooves are symmetrically arranged relative to the ring K1, and the vanes (3) are respectively arranged on the; a ring groove is formed in the side wall of the rotor (2) at the middle position, left sliding grooves which are in one-to-one correspondence with the left positioning grooves are formed in the left side face of the ring groove, right sliding grooves which are in one-to-one correspondence with the right positioning grooves are formed in the right side face of the ring groove, and blades (3) on the left positioning grooves are further arranged on the left sliding grooves in a sliding mode and sealed through sealing elements; the blade (3) on the right positioning groove is also arranged on the right sliding groove in a sliding manner and is sealed by a sealing element; the ring K1 is clamped between the blade (3) on the left positioning groove and the blade (3) on the right positioning groove, a containing cavity is formed between two adjacent blades (3), the surface of the ring groove, the inner wall of the shell (1) and the side wall of the ring K1, oil ports with the same number as the containing cavities are formed in the rotor (2), one oil port is communicated with one containing cavity, and the two ends of the rotor (2) are connected with oil distribution blocks (4); the outer wall of the shell (1) is provided with a convex circular ring J1, and the convex circular ring J1 is placed in the guide groove of the guide block (6); the axis of the rotor (2) and the axis of the shell (1) are not coincident;

when rotor (2) rotated, rotor (2) drove blade (3) and rotate together, at the rotation in-process, and blade (3) on left spout and the right spout are periodic accomplishes concertina movement for the volume that holds the chamber takes place periodic change, and then periodic formation high pressure holds chamber and low pressure and holds the chamber, and the low pressure holds the chamber and passes through oil distribution piece (4) oil absorption, and the high pressure holds the chamber and passes through oil distribution piece (4) oil extraction.

2. A double acting variable capacity vane pump according to claim 1, wherein in the rotor (2) is a waist drum shaped table a2 with two spherical crowns cut off in parallel at both ends, the two ends of the table a2 are a conical side C2 and a conical side D2, the table a2, the conical side C2 and the conical side D2 form ring grooves; the conical side surface C2 is provided with grooves E2 which are in one-to-one correspondence with the right positioning grooves, the grooves E2 are evenly divided into the conical side surface C2, and the grooves E2 are right sliding grooves; the conical side surface D2 is provided with grooves F2 which correspond to the left positioning grooves one by one, the conical side surface D2 is equally divided, and the groove F2 is a left sliding groove; a hole K2 is formed between two adjacent grooves E2 on the conical side surface C2, a hole K2 ' is formed between two adjacent grooves F2 on the conical side surface D2, the surface connected with the conical side surface C2 is a spherical surface G2, the surface connected with the conical side surface D2 is a spherical surface H2, the radiuses and the spherical centers of the spherical surfaces G2 and H2 are the same as the radius and the spherical center of the spherical surface A1 in the shell (1), two end surfaces of the rotor (2) are a circular ring surface I2 and a circular ring surface J2, holes L2 corresponding to the holes K2 are uniformly distributed on the circular ring surface I2, holes L2 ' corresponding to the holes K2 ' are uniformly distributed on the circular ring surface J2, and the holes L2 are communicated with the holes K2 corresponding to the holes, so that a second oil port is formed for oil feeding or oil discharging; the hole L2 ' is communicated with the hole K2 ' corresponding to the hole L2 ' to form a first oil port for oil feeding or oil discharging.

3. A double acting variable capacity vane pump as claimed in claim 2 wherein the cross-sectional shapes of the groove E2 and the groove F2 are each formed by connecting a conical plane S2, an arc P2 and a conical plane M2 in this order, the outer ends of the conical plane S2 and the conical plane M2 are each connected with an arc R2, the two arcs R2 are concentric, and a seal is installed in each arc R2.

4. A double acting variable capacity vane pump according to claim 3, wherein the sealing member comprises a gasket (7) and a flexible sealing strip (8), one flexible sealing strip (8) and one gasket (7) are placed on each circular arc R2 from inside to outside in sequence, and the two gaskets (7) are respectively located on both sides of one vane (3) and abut against the vane (3);

or the cushion block (7) and the elastic sealing strip (8) can be combined into a whole to be placed in the circular arc R2.

5. A double acting variable capacity vane pump according to claim 4, characterized in that the pad (7) is elongated and has a crescent-shaped cross-section, the length of which is equal to the radial length of the ring K1;

the elastic sealing strip (8) is long-strip-shaped, the cross section of the elastic sealing strip is semicircular, the radius of the outer circle of the elastic sealing strip is the same as that of the circular arc R2, the radius of the inner circle of the elastic sealing strip is the same as that of the crescent of the cushion block (7), and the length of the elastic sealing strip is equal to the radial length of the circular ring K1.

6. A double acting variable capacity vane pump according to any one of claims 2 to 5, wherein the housing (1) has an inner spherical surface A1 and an outer spherical surface B1, both the inner spherical surface A1 and the outer spherical surface B1 are waist drum shaped spherical surfaces with both ends cut off spherical caps of the same size in parallel, the center of the inner spherical surface A1 is extended toward the center of the sphere with a circle of circle K1, the circle K1 is flanked by two parallel circle planes C1 and D1, the circle K1 is centered on the inner spherical surface E1, and the diameter of the circle is equal to the diameter of the table A2; at least three grooves P1 are uniformly formed on the inner wall of the shell (1) along the circumferential direction, namely a left positioning groove; the inner wall of the shell (1) is uniformly provided with grooves P1 ' which are in one-to-one correspondence with the left positioning grooves along the circumferential direction, namely the right positioning grooves, the grooves P1 and the grooves P1 ' are symmetrically arranged about a circular ring K1, the widths of the grooves P1 and the grooves P1 ' are the same as the thickness of the blades (3), and the middle part of an outer spherical surface B1 protrudes outwards for a circle of circular ring J1.

7. A double acting variable capacity vane pump as claimed in claim 6 wherein the vanes (3) are enclosed by front and rear parallel planes A3, B3, upper and lower cylindrical surfaces C3, D3, one side and the other side long cylindrical surface F3; the radius and the center of a circle of the cylindrical surface C3 are respectively the same as those of the groove bottom surface of the groove P1 or the groove P1' on the shell (1), and the radius and the center of a circle of the cylindrical surface D3 are respectively the same as those of the ball table A2; the long cylindrical surface F3 is hinged on the sliding shoe (5).

8. A double acting variable capacity vane pump as claimed in claim 7, wherein the oil distribution block (4) is a cylinder having an outer cylindrical surface A4 of diameter equal to the diameter of the circular surfaces I2 and J2 at the two ends of the rotor (2), and two kidney-shaped through holes B4 and C4 are formed in the cylinder, one kidney-shaped through hole communicating with the high pressure chamber and the other kidney-shaped through hole communicating with the low pressure chamber.

9. A double acting variable capacity vane pump as claimed in claim 8, wherein the outer tips of the vanes (3) are mounted on shoes (5), the shoes (5) being in side abutment with the ring K1.

10. A double acting variable capacity vane pump as claimed in claim 9 wherein the slipper (5) is elongated and is enclosed by two parallel planes a5, B5, an upper spherical surface C5, a lower spherical surface D5, a bottom surface E5 and another concave cylindrical surface F5; the radius and the center of the outer spherical surface C5 are the same as those of an inner spherical surface A1 of the shell (1), the radius and the center of the lower spherical surface D5 are the same as those of a spherical surface A2 of the rotor (2), and the radius and the center of the concave cylindrical surface F5 are the same as those of a long cylindrical surface F3 of the blade (3); the bottom surface E5 abuts on the annular flat surface C1 or the annular flat surface D1 of the annular ring K1.