CN109185125B - High-performance variable multi-vane pump - Google Patents
High-performance variable multi-vane pump Download PDFInfo
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- CN109185125B CN109185125B CN201811142348.9A CN201811142348A CN109185125B CN 109185125 B CN109185125 B CN 109185125B CN 201811142348 A CN201811142348 A CN 201811142348A CN 109185125 B CN109185125 B CN 109185125B
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- 238000010521 absorption reaction Methods 0.000 claims description 2
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 238000007599 discharging Methods 0.000 claims description 2
- 238000000605 extraction Methods 0.000 claims description 2
- 238000007789 sealing Methods 0.000 description 4
- 238000010276 construction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
The invention discloses a high-performance variable multi-vane pump, which comprises a shell, a rotor, vanes and a sliding shoe, wherein the shell covers the outside of the rotor, the shell is hemispherical, the end surface of the shell inwards extends to form a circle of ring K1, and the ring K1 passes through the spherical center of the shell; the rotor is at least provided with three sliding grooves which are uniformly distributed along the circumferential direction, the sliding grooves are provided with blades in a sliding manner, the outer ends of the blades are arranged on sliding shoes, and the sliding shoes are abutted against the side face of the ring K1; a cavity is formed between every two adjacent blades, the surface of the rotor, the inner wall of the shell and the side wall of the circular ring K1; the axis of the rotor and the axis of the housing do not coincide; the invention has the advantages of small relative linear velocity of the blade and the shell, extremely high speed operation, small volume, large discharge capacity and high output pressure.
Description
Technical Field
The invention relates to a multi-vane pump, in particular to a high-performance variable multi-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 high-performance variable multi-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 very small, the pump can run at a very high speed, the volume is very small, the discharge capacity is very large, and the output pressure is very high.
In order to achieve the purpose, the technical scheme adopted by the invention is as follows: a high-performance variable multi-vane pump is characterized by comprising a shell, a rotor, vanes, an oil distribution block, a sliding shoe and a guide block, wherein the rotor is positioned in the center, the shell covers the outside of the rotor, the shell is hemispherical, a circle of ring K1 extends inwards from the end surface of the shell, and the ring K1 passes through the spherical center of the shell; the rotor is at least provided with three sliding grooves which are uniformly distributed along the circumferential direction, the sliding grooves are provided with blades in a sliding manner, the outer ends of the blades are arranged on sliding shoes, and the sliding shoes are abutted against the side face of the ring K1; a cavity is formed between every two adjacent blades, the surface of the rotor, the inner wall of the shell and the side wall of the ring K1, oil ports with the same number as the cavities are formed in the rotor, one oil port is communicated with one cavity, and one end of the rotor is connected with an oil distribution 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, the sliding shoes rotate around the axis of the ring K1 due to the fact that the sliding shoes are abutted to the side face of the ring K1, the blades on the sliding grooves periodically complete telescopic motion, the volume of the containing cavity is periodically changed, then the high-pressure containing cavity and the 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 spherical crowns cut off at two ends is arranged in the rotor, at least three grooves B2 are formed in the ball table A2, the ball table A2 is divided equally, the width of each groove B2 is the same as the thickness of each blade, and one end of the ball table A2 is a conical side surface C2; the conical side surface C2 is provided with grooves E2 with the same number as the grooves B2, the grooves E2 are evenly divided into the conical side surface C2, and the grooves E2 are sliding grooves; the groove B2 is communicated with the bottom of the groove E2; the width of the groove E2 and the width of the groove F2 are the same as the thickness of the blade, a hole K2 is arranged between two adjacent grooves E2 on the conical side surface C2, the surface connected with the conical side surface C2 is a spherical surface G2, the radius and the spherical center of the spherical surface G2 are the same as those of the spherical surface A1 in the shell, one end surface of the rotor is a circular ring surface I2, holes L2 corresponding to the holes K2 are uniformly distributed on the circular ring surface I2, and the holes L2 are communicated with the holes K2 corresponding to the holes L2 to form oil ports for oil inlet or oil discharge.
Furthermore, the shell is hemispherical and 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 spherical crowns of different sizes cut off at two ends in parallel, a circle of circular ring K1 extends towards the spherical center direction at the end surface of the inner spherical surface A1, and the circular ring K1 passes through the spherical center of the inner spherical surface A1; the two sides of the ring K1 are two parallel ring planes C1 and D1, and the middle of the ring K1 is an inner circular spherical surface E1, the diameter of which is equal to that of the table A2.
Further, the outer wall of the housing has a convex ring J1, and the convex ring J1 is received in the guide groove of the guide block.
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 spherical surface A1 in the shell, and the radius and the center of the cylindrical surface D3 are respectively the same as those of the bottom surface of the groove B2 on the spherical surface of the rotor; 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 diameter of the circular surface I2 at one end 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.
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.
Furthermore, the hole K2 on the conical side surface C2 of the rotor may be opened on the circular ring K1 of the spherical surface a1 in the housing instead of the conical side surface C2 of the rotor, and accordingly, the oil distribution block is not located at one end of the rotor, but located at one end of the circular ring K1 of the housing.
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 pump body is very low, and the rotor and the pump body can run at extremely high speed;
6) the structure is compact, and the processing is relatively easy;
7) low cost and long service life.
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 right side view 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;
in the figure: 1. the structure comprises a shell, 2. a rotor, 3. blades, 4. an oil distribution block, 5. a sliding shoe and 6. a guide block.
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, the embodiment of the present invention provides a high performance variable multiple vane pump, which includes a casing 1, a rotor 2, vanes 3, an oil distribution block 4, and a slipper 5, wherein the rotor 2 is located at the center, the casing 1 covers the outside of the rotor 2, the casing 1 is hemispherical, a ring K1 extends inwards from the end surface of the casing 1, and the ring K1 passes through the spherical center of the casing 1; the rotor 2 is at least provided with three sliding grooves which are uniformly distributed along the circumferential direction, the sliding grooves are provided with blades 3 in a sliding manner, the outer end heads of the blades 3 are arranged on sliding shoes 5, and the sliding shoes 5 are abutted against the side surface of the circular ring K1; a cavity is formed between two adjacent blades 3, the surface of the rotor 2, the inner wall of the shell 1 and the side wall of the ring K1, oil ports with the same number as the cavities are formed in the rotor 2, one oil port is communicated with one cavity, and one end of the rotor 2 is connected with an oil distribution block 4; 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, because piston shoes 5 and ring K1 side butt, piston shoes 5 rotates round ring K1's axis, and the periodic completion concertina movement of blade 3 on the 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 the low pressure, and the low pressure holds the chamber and passes through the 4 oil absorptions of oil distribution piece, and the high pressure holds the chamber and passes through the 4 oil extraction of oil distribution piece.
It should be noted that the number of the blades 3 is at least 3, the number of the sliding grooves and the sliding shoes are the same as the number of the blades 3, and the number of the blades 3 is 9 as an example to further illustrate the specific embodiment of the present invention, and those skilled in the art can obtain other embodiments of the number of the blades 3 without any doubt according to 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 hemispherical and 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 spherical crowns of different sizes cut off at two ends in parallel, a circle of circular ring K1 extends towards the spherical center direction at the end face of the inner spherical surface A1, and the circular ring K1 passes through the spherical center of the inner spherical surface A1; two parallel circular planes C1 and D1 are arranged on two sides of the circular ring K1, an inner circular spherical surface E1 is arranged in the middle of the circular ring K1, and the diameter of the inner circular spherical surface E1 is equal to that of the ball table A2; preferably, a circle of ring J1 protrudes from the middle of the outer spherical surface B1, the housing 1 can be stationary during actual operation, and in order to reduce the relative rotation speed of the housing 1 and the rotor 2, the convex ring J1 is placed in the guide groove of the guide block 6, and the convex ring J1 can rotate under the drive of external force or not drive the external force. The middle part of the outer spherical surface B1 protrudes outwards to form a ring J1, which is similar to the outward extension of the ring K1. The ring K1 and the ring J1 form a large ring, which may be separated from the casing 1 and formed as a swash plate, and the left and right halves of the casing 1 are fixed to the swash plate in close contact therewith.
Fig. 3a and 3b are schematic views showing the shape and structure of the rotor 2 of the present invention. The middle of the rotor (2) is a waist drum-shaped table A2 with two parallel truncated spherical crowns at two ends, nine grooves B2 are formed in the table A2, the table A2 is divided equally, the width of each groove B2 is the same as the thickness of each blade (3) like the longitude lines of a globe, and one end of the table A2 is a conical side surface C2; the conical side surface C2 is provided with grooves E2 with the same number as the grooves B2, the grooves E2 are evenly divided into the conical side surface C2, and the grooves E2 are sliding grooves; the groove B2 is communicated with the bottom of the groove E2; the widths of the grooves E2 and the grooves F2 are the same as the thickness of the blades (3), a hole K2 is formed between every two adjacent grooves E2 on the conical side surface C2, the surface connected with the conical side surface C2 is a spherical surface G2, the radius and the spherical center of the spherical surface G2 are the same as those of the spherical surface A1 in the shell (1), one end surface of the rotor (2) is a circular ring surface I2, holes L2 corresponding to the holes K2 are uniformly distributed on the circular ring surface I2, and the holes L2 are communicated with the holes K2 corresponding to the holes to form oil ports for oil feeding or oil discharging. Of course, the shape of each of the holes L2 and K2 may be circular, rectangular, trapezoidal, or the like. It should be noted that the hole K2 on the conical side surface C2 of the rotor 2 may be formed on the ring K1 of the spherical surface a1 in the housing 1 instead of the conical side surface C2 of the rotor 2, and accordingly, the oil distribution block 4 is not located at one end of the rotor 2, but at one end of the ring K1 of the housing 1.
Fig. 4a and 4b are schematic views of the shape and structure of the blade 3 of the present invention. The blades 3 share the same 9 pieces, 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 the radius and the center of the spherical surface A1 in the shell 1, and the radius and the center of the cylindrical surface D3 are respectively the same as the radius and the center of the bottom surface of the groove B2 on the spherical surface of the rotor 2; the oblong cylindrical surface F3 is hinged to the slipper 5, as shown in fig. 7. The rotor 2 may not have the groove B2 in the ball land a2, and the groove E2 and the groove F2 are independent of each other; the cylindrical surface D3 abuts the surface of the ball table a2, and the radius and center of the cylindrical surface D3 are the same as those of the ball table a2 of the rotor 2, respectively.
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 surface I2 at one end 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. 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.
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:
as shown in fig. 1, a closed cavity is formed between two adjacent vanes 3, the surface of the rotor 2, the inner wall of the casing 1 and the side wall of the ring K1, and 9 cavities are formed in total;
at the uppermost end, as shown in figure 1, the casing 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 blade 3 to rotate together, because the sliding shoe 5 is abutted against the side face of the ring K1, the sliding shoe 5 rotates around the axis of the ring K1, the blade 3 on the sliding groove periodically completes telescopic motion, so that the volume of the accommodating cavity is periodically changed, the volume of the accommodating cavity at the lowest end of the pump is gradually increased from the minimum, the accommodating cavity is disconnected from the high-pressure cavity and is communicated with the low-pressure cavity through the oil distribution block 4 at the right side, and the accommodating cavity starts to absorb oil through the oil distribution block 4 at the right side. 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 be reduced, the containing cavity is disconnected from the low-pressure cavity and communicated with the high-pressure cavity through the oil distribution block 4 on the right side, and the containing cavity begins to discharge oil through the oil distribution block 4 on the right side. 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.
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 (8)
1. A high-performance variable multi-vane pump is characterized by comprising a shell (1), a rotor (2), vanes (3), an oil distribution block (4) and a sliding shoe (5), wherein the rotor (2) is positioned at the center, the shell (1) covers the outer part of the rotor (2), the shell (1) is hemispherical, a circle of ring K1 extends inwards from the end surface of the shell (1), and the ring K1 passes through the spherical center of the shell (1); the rotor (2) is at least provided with three sliding grooves which are uniformly distributed along the circumferential direction, the sliding grooves are provided with blades (3) in a sliding manner, the outer ends of the blades (3) are arranged on sliding shoes (5), and the sliding shoes (5) are abutted against the side surface of the ring K1; a containing cavity is formed among the adjacent two blades (3), the surface of the rotor (2), the inner wall of the shell (1) and the side wall of the circular 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 one end of the rotor (2) is connected with an oil distribution block (4); 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, because piston shoes (5) and ring K1 side butt, piston shoes (5) rotated round ring K1's axis, blade (3) periodic completion concertina movement on the 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 the low pressure, the low pressure holds the chamber and passes through oil distribution block (4) oil absorption, the high pressure holds the chamber and passes through oil distribution block (4) oil extraction.
2. A high performance variable multiple vane pump according to claim 1 wherein the rotor (2) is a waist drum shaped table a2 with two spherical crowns truncated in parallel at both ends, the table a2 has at least three grooves B2, equally dividing the table a2, the width of the grooves B2 is the same as the thickness of the vanes (3), and one end of the table a2 is a conical side C2; the conical side surface C2 is provided with grooves E2 with the same number as the grooves B2, the grooves E2 are evenly divided into the conical side surface C2, and the grooves E2 are sliding grooves; the groove B2 is communicated with the bottom of the groove E2; the widths of the grooves E2 and the grooves B2 are the same as the thickness of the blades (3), a hole K2 is formed between every two adjacent grooves E2 on the conical side surface C2, the surface connected with the conical side surface C2 is a spherical surface G2, the radius and the spherical center of the spherical surface G2 are the same as those of the spherical surface A1 in the shell (1), one end surface of the rotor (2) is a circular ring surface I2, holes L2 corresponding to the holes K2 are uniformly distributed on the circular ring surface I2, and the holes L2 are communicated with the holes K2 corresponding to the holes to form oil ports for oil feeding or oil discharging.
3. A high performance variable multiple vane pump according to claim 2 wherein the housing (1) is hemispherical and has 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 spherical crowns of different sizes cut off at two ends in parallel, a circle of ring K1 extends towards the center of the sphere at the end surface of the inner spherical surface a1, and the ring K1 crosses the center of the inner spherical surface a 1; the two sides of the ring K1 are two parallel ring planes C1 and D1, and the middle of the ring K1 is an inner circular spherical surface E1, the diameter of which is equal to that of the table A2.
4. A high performance variable capacity multiple vane pump according to claim 3 wherein the outer wall of the housing (1) has a convex ring J1, the convex ring J1 being received in the guide groove of the guide block (6).
5. A high-performance variable multi-vane pump according to claim 3 or 4, characterized in that the vanes (3) are enclosed by front and rear parallel planes A3, B3, upper and lower cylindrical surfaces C3, D3, and a side and other side cylindrical surface F3; the radius and the center of a cylindrical surface C3 are respectively the same as those of a spherical surface A1 in the shell (1), and the radius and the center of a cylindrical surface D3 are respectively the same as those of the bottom surface of a groove B2 on the spherical surface of the rotor (2); the long cylindrical surface F3 is hinged on the sliding shoe (5).
6. A high-performance variable multi-vane pump according to claim 5, characterized in that 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 surface I2 at one end 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 chamber, and the other kidney-shaped through hole is communicated with the low-pressure chamber.
7. A high performance variable multiple vane pump according to claim 6 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.
8. A high performance variable capacity multiple vane pump according to claim 2 wherein the bore K2 in the conical side C2 of the rotor (2) may be open not in the conical side C2 of the rotor (2) but in the ring K1 of the spherical surface a1 in the housing (1), and correspondingly the oil distribution block (4) is not located at the rotor (2) end but at the ring K1 end of the housing (1).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811142348.9A CN109185125B (en) | 2018-09-28 | 2018-09-28 | High-performance variable multi-vane pump |
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| CN201811142348.9A CN109185125B (en) | 2018-09-28 | 2018-09-28 | High-performance variable multi-vane pump |
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| CN109185125A CN109185125A (en) | 2019-01-11 |
| CN109185125B true CN109185125B (en) | 2020-02-07 |
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| CN110131160B (en) * | 2019-05-29 | 2020-08-11 | 河南航天液压气动技术有限公司 | Variable displacement vane pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101605995A (en) * | 2007-04-10 | 2009-12-16 | 博格华纳公司 | The variable-displacement dual vane pump |
| CN201535245U (en) * | 2009-03-12 | 2010-07-28 | 杨连才 | Partition board type rotor rotation device |
| CN103671095A (en) * | 2013-12-16 | 2014-03-26 | 浙江大学 | Multiple-blade hydraulic pump |
| JP2014070545A (en) * | 2012-09-28 | 2014-04-21 | Kayaba Ind Co Ltd | Variable displacement vane pump |
| CN103939335A (en) * | 2013-12-23 | 2014-07-23 | 马江 | Double-action variable vane impeller pump or motor |
-
2018
- 2018-09-28 CN CN201811142348.9A patent/CN109185125B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101605995A (en) * | 2007-04-10 | 2009-12-16 | 博格华纳公司 | The variable-displacement dual vane pump |
| CN201535245U (en) * | 2009-03-12 | 2010-07-28 | 杨连才 | Partition board type rotor rotation device |
| JP2014070545A (en) * | 2012-09-28 | 2014-04-21 | Kayaba Ind Co Ltd | Variable displacement vane pump |
| CN103671095A (en) * | 2013-12-16 | 2014-03-26 | 浙江大学 | Multiple-blade hydraulic pump |
| CN103939335A (en) * | 2013-12-23 | 2014-07-23 | 马江 | Double-action variable vane impeller pump or motor |
Also Published As
| Publication number | Publication date |
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| CN109185125A (en) | 2019-01-11 |
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