CN114198276A - Screw reciprocating hydraulic piston pump - Google Patents
Screw reciprocating hydraulic piston pump Download PDFInfo
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- CN114198276A CN114198276A CN202111520160.5A CN202111520160A CN114198276A CN 114198276 A CN114198276 A CN 114198276A CN 202111520160 A CN202111520160 A CN 202111520160A CN 114198276 A CN114198276 A CN 114198276A
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- 230000003247 decreasing effect Effects 0.000 claims abstract description 4
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims description 3
- 238000005485 electric heating Methods 0.000 claims 1
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 238000006073 displacement reaction Methods 0.000 abstract description 2
- 238000007599 discharging Methods 0.000 description 8
- 238000004891 communication Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
- F04B3/003—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage with two or more pistons reciprocating one within another, e.g. one piston forning cylinder of the other
- F04B3/006—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage with two or more pistons reciprocating one within another, e.g. one piston forning cylinder of the other with rotating cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The spiral reciprocating hydraulic piston pump comprises an outer shell, wherein an oil suction port and an oil discharge port are formed in the outer wall of the outer shell; the left end cover, the outer shell and the right end cover jointly enclose a pump cavity, and an inner shell lining is arranged in the pump cavity; the left section and the right section of the inner shell lining are respectively provided with n/2 first waist-shaped oil ports and n/2 second waist-shaped oil ports; a left piston and a right piston of a flow distribution cylinder body are arranged in the inner shell lining, n rectangular grooves are uniformly distributed on the flow distribution cylinder body along the circumferential direction, and the rectangular grooves are divided into a left rectangular groove and a right rectangular groove; a left suction and discharge oil cavity is formed by enclosing the left piston, the flow distribution cylinder body and the cylindrical plunger, and a right suction and discharge oil cavity is formed by enclosing the cylindrical plunger, the flow distribution cylinder body and the right piston; the left rectangular groove and the right rectangular groove on the flow distribution cylinder body are respectively communicated with the first waist-shaped oil port and the second waist-shaped oil port on the inner shell lining, the oil cavity with gradually increased volume absorbs oil, and the oil cavity with gradually decreased volume discharges oil. The invention has simple structure and low manufacturing cost, and the volume is greatly reduced compared with the hydraulic pump with the same displacement.
Description
Technical Field
The invention relates to the field of fluid transmission and control, in particular to a spiral reciprocating type hydraulic piston pump.
Background
The hydraulic pump is an indispensable core power element in the hydraulic system, and the performance of the hydraulic pump directly affects the stability and reliability of the hydraulic system. In recent years, the fields of aviation, aerospace, navigation and the like in China are rapidly developed, and the fields of high technology and high precision put forward higher requirements on the performance of the hydraulic pump.
The traditional plunger pump has the disadvantages of large quantity of internal parts, high manufacturing process requirement and complex structure; the plunger pump is sensitive to pollution of oil, the maintenance cost is high, three pairs of friction pairs are arranged in the traditional plunger pump, the number of the friction pairs is large, the friction pairs can be limited by a PV value (product of pressure and speed), when the centrifugal force moment of a plunger piston shoe is larger than the cylinder body spring moment in a high-speed motion state, the cylinder body can overturn, the gap between the cylinder body and a valve plate is enlarged, leakage can occur to cause pressure loss, the performance of the plunger pump and the stability of a hydraulic system can be seriously influenced, and therefore the traditional plunger pump is not suitable for running under a high-speed working condition.
Disclosure of Invention
To overcome the above problems, the present invention provides a spiral reciprocating hydraulic piston pump.
The technical scheme adopted by the invention is as follows: the spiral reciprocating hydraulic piston pump comprises an outer shell, wherein the left end and the right end of the outer shell are respectively connected with a left end cover and a right end cover, and the left end cover and the right end cover are provided with coaxial shaft holes; an oil suction port is arranged on the left side of the outer wall of the outer shell, and an oil discharge port is arranged on the right side of the outer wall of the outer shell; the left end cover, the outer shell and the right end cover jointly enclose a pump cavity, and an inner shell lining is arranged in the pump cavity;
the middle part of the outer wall of the inner shell lining is provided with a step, and the step divides the outer wall of the inner shell lining into a left section and a right section; the step is provided with a groove, and an O-shaped ring is arranged in the groove and used for separating oil liquid of the left section and the right section; the left section and the right section of the inner shell lining are respectively provided with n/2 first waist-shaped oil ports and n/2 second waist-shaped oil ports, the first waist-shaped oil ports are communicated with the oil suction port, and the second waist-shaped oil ports are communicated with the oil discharge port; the first waist-shaped oil port and the second waist-shaped oil port are uniformly distributed and staggered along the circumferential direction, and oil enters or is discharged through the first waist-shaped oil port and the second waist-shaped oil port; the right end of the right section of the inner shell lining is provided with a first small hole which is fixedly connected with the central shaft;
a left piston and a right piston of a flow distribution cylinder body are arranged in the inner shell lining, n rectangular grooves are uniformly distributed on the flow distribution cylinder body along the circumferential direction, each rectangular groove is divided into a left rectangular groove and a right rectangular groove, a left through hole is formed in the bottom of the left side groove of the left rectangular groove, and a right through hole is formed in the bottom of the right side groove of the right rectangular groove; the left rectangular grooves and the right rectangular grooves are arranged in a staggered mode and are communicated with the suction and exhaust oil cavities and the right suction and exhaust oil cavities respectively; the left end and the right end in the flow distribution cylinder body are respectively connected with a left piston and a right piston, the left piston and the right piston are in interference fit with the flow distribution cylinder body, and the left piston is connected with a high-speed motor through a coupler;
a central shaft is arranged in the left piston, the flow distribution cylinder body and the right piston, and two ends of the central shaft are respectively arranged in shaft holes of the left end cover and the right end cover; a second small hole is formed in the position, corresponding to the first small hole, of the right end of the central shaft, and cylindrical pins are arranged in the first small hole and the second small hole and connect the central shaft with the inner shell lining together;
a cylindrical plunger is arranged in the middle of the central shaft, turn-back threads are respectively arranged on the central shaft and positioned on the left side and the right side of the cylindrical plunger, and the turn-back threads are formed by overlapping two threads with opposite rotation directions; the left piston and the right piston are provided with crescent teeth corresponding to the turn-back thread, and the crescent teeth are matched with the thread groove of the turn-back thread; the flow distribution cylinder body is driven by a high-speed motor to rotate, so that a left piston and a right piston are driven to rotate; when the left piston and the right piston rotate, the left piston and the right piston are subjected to the force of the returning threads, so that the left piston, the flow distribution cylinder body and the right piston are driven to perform axial reciprocating motion while rotating;
a left suction and discharge oil cavity is formed by enclosing the left piston, the flow distribution cylinder body and the cylindrical plunger, and a right suction and discharge oil cavity is formed by enclosing the cylindrical plunger, the flow distribution cylinder body and the right piston; the left suction and discharge oil cavity and the right suction and discharge oil cavity change along with the axial reciprocating motion of the left piston, the flow distribution cylinder body and the right piston; when the left piston, the flow distribution cylinder body and the right piston move from the leftmost end to the rightmost end, the volume of the left suction and discharge oil cavity is gradually reduced, and the volume of the right suction and discharge oil cavity is gradually increased; conversely, when the left piston, the flow distribution cylinder body and the right piston move from the rightmost end to the leftmost end, the volume of the right suction and discharge oil cavity is gradually reduced, and the volume of the left suction and discharge oil cavity is gradually increased;
the left rectangular groove and the right rectangular groove on the flow distribution cylinder body are respectively communicated with the first waist-shaped oil port and the second waist-shaped oil port on the inner shell lining, the oil cavity with gradually increased volume absorbs oil, and the oil cavity with gradually decreased volume discharges oil.
Furthermore, the angle between the n rectangular grooves is 360 degrees/n, and the opening degree of the rectangular grooves is 360 degrees/2 n.
The working principle of the invention is as follows:
the high-speed motor is connected with a left piston connecting shaft through a coupler to drive the left piston, the right piston and the flow distribution cylinder body to rotate, the left piston and the right piston can generate axial reciprocating motion under the action of a return thread in the rotating process, when the left piston and the right piston start to move, the rotating angle is 0 degrees, the pistons are positioned at the leftmost ends, the left suction and discharge oil cavity is positioned at the maximum volume, the right suction and discharge oil cavity is positioned at the minimum volume, and the window of the flow distribution cylinder body is not communicated with the suction and discharge oil port of the inner shell lining; when the rotation angle is rotated to 360 degrees/2 n from 0 degree, the window of the flow distribution cylinder body is communicated with the oil port of the pump shell, the left piston and the right piston start to move rightwards, the volume of the left suction and discharge oil cavity is reduced, oil is discharged from the oil discharge port, the volume of the right suction and discharge oil cavity is increased, and oil suction is started; when the cylinder rotates to 360 degrees/2 n, the volumes of the left cavity and the right cavity are equal, and the window of the flow distribution cylinder body is completely communicated with the oil port of the lining of the inner shell; when the rotation angle is from 360 degrees/2 n to 360 degrees/n, the piston continues to move rightwards, the left oil suction and discharge cavity continues to discharge oil, the right oil suction and discharge cavity continues to suck oil, and the window of the flow distribution cylinder body is communicated with the oil port of the inner shell lining from complete communication to non-communication; when the rotation angle is from 360 degrees/n to 3 degrees (360 degrees/2 n), the window of the flow distribution cylinder body is communicated with the oil port of the inner shell lining, the piston starts to move leftwards, the left oil suction and discharge cavity starts to suck oil, the right oil suction and discharge cavity starts to discharge oil, when the piston rotates to 3 degrees (360 degrees/2 n), the volumes of the left cavity and the right cavity are equal, and the window of the flow distribution cylinder body is completely communicated with the oil port of the inner shell lining; when the rotation angle is from 3 to 4, the piston continues to move leftwards, the left suction and discharge oil cavity continues to suck oil, the right suction and discharge oil cavity continues to discharge oil, and when the piston rotates to 4, the volume of the left suction and discharge oil cavity reaches the maximum, and the window of the flow distribution cylinder body is communicated with the oil port of the inner shell lining from complete to no communication; thus, one oil sucking and discharging period is completed, so that when the oil sucking and discharging device rotates for one circle, oil sucking and discharging can be performed for n/2 times, and the oil discharging amount is greatly increased.
The invention has the beneficial effects that:
1. the spiral reciprocating hydraulic piston pump has fewer parts, simple structure and low manufacturing cost;
2. in the process of rotating for one circle, oil suction and discharge can be carried out for n/2 times, so that the oil suction and discharge capacity is greatly increased, and the volume is greatly reduced compared with a hydraulic pump with the same discharge capacity;
3. the displacement of the piston pump can be easily adjusted by changing the pitch, the length and the like of the turn-back thread.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic view of the present invention with the pump housing removed;
FIG. 3 is a schematic view of the inner shell liner of the present invention;
FIG. 4 is a schematic view of a distribution cylinder according to the present invention;
FIG. 5 is a schematic view of a mandrel according to the present invention;
FIG. 6a shows the distribution of the flow from 0 to 360/2 n according to the present invention;
FIG. 6b shows the flow distribution of the present invention when the angle of 360/2 n is 360/n;
FIG. 6c shows the flow distribution of the present invention when the flow distribution is rotated by 360/n to 3 x (360/2 n);
FIG. 6d shows the distribution of the flow from 3 x (360/2 n) to 4 x (360/2 n) according to the present invention;
description of reference numerals: 1. the oil pump comprises an outer shell, 2, a left end cover, 3, a right end cover, 4, an inner shell lining, 5, a flow distribution cylinder body, 6, a central shaft, 7, a left piston, 8, a left piston, 9, an annular groove, 10, a waist-shaped oil port, 11, small holes, 12, a rectangular groove, 13, a turn-back thread, 14, a cylindrical plunger, 15, small holes, 16, a left suction and discharge oil cavity, 17 and a right suction and discharge oil cavity.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are only some embodiments, but not all embodiments, of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that the orientations or positional relationships indicated as the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., appear based on the orientations or positional relationships shown in the drawings only for the convenience of describing the present invention and simplifying the description, but not for indicating or implying that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" as appearing herein are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly stated or limited, the terms "mounted," "connected," and "connected" should be interpreted broadly, e.g., as being fixed or detachable or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Referring to the attached drawings, the spiral reciprocating hydraulic piston pump comprises an outer shell 1, wherein the left end and the right end of the outer shell 1 are respectively connected with a left end cover 2 and a right end cover 3, and the left end cover 2 and the right end cover 3 are provided with coaxial shaft holes; an oil suction port is arranged on the left side of the outer wall of the outer shell 1, and an oil discharge port is arranged on the right side of the outer wall of the outer shell 1; the left end cover 2, the outer shell 1 and the right end cover 3 jointly enclose a pump cavity, and an inner shell lining 4 is arranged in the pump cavity;
the middle part of the outer wall of the inner shell lining 4 is provided with a step, and the step divides the outer wall of the inner shell lining 4 into a left section and a right section; a groove 9 is formed in the step, and an O-shaped ring is arranged in the groove 9 and used for separating oil liquid of the left section and the right section; the left section and the right section of the inner shell lining 4 are respectively provided with n/2 first waist-shaped oil ports 10a and n/2 second waist-shaped oil ports 10b, the first waist-shaped oil ports 10a are communicated with the oil suction port, and the second waist-shaped oil ports 10b are communicated with the oil discharge port; the first waist-shaped oil port 10a and the second waist-shaped oil port 10b are uniformly distributed along the circumferential direction and are arranged in a staggered manner, and oil enters or is discharged through the first waist-shaped oil port 10a and the second waist-shaped oil port 10 b; the right end of the right section of the inner shell lining 4 is provided with a first small hole 11 which is fixedly connected with the central shaft;
the inner shell bushing 4 is internally provided with a left piston 7 and a right piston 8 of a flow distribution cylinder body 5, n rectangular grooves 12 are uniformly distributed on the flow distribution cylinder body 5 along the circumferential direction, the angle formed by the n rectangular grooves 12 is 360 degrees/n, and the opening degree of each rectangular groove is 360 degrees/2 n. The rectangular groove 12 is divided into a left rectangular groove and a right rectangular groove, a left through hole is formed in the bottom of the left side groove of the left rectangular groove, and a right through hole is formed in the bottom of the right side groove of the right rectangular groove; the left rectangular grooves and the right rectangular grooves are arranged in a staggered mode and are communicated with the suction and exhaust oil cavities 16 and the right suction and exhaust oil cavities 17 respectively; the left end and the right end in the flow distribution cylinder body 5 are respectively connected with a left piston 7 and a right piston 8, the left piston 7 and the right piston 8 are in interference fit with the flow distribution cylinder body 5, and the left piston 7 is connected with a high-speed motor through a coupler; (ii) a
A central shaft 6 is arranged in the left piston 7, the flow distribution cylinder body 5 and the right piston 8, and two ends of the central shaft 6 are respectively arranged in shaft holes of the left end cover 2 and the right end cover 3; a second small hole 15 is formed in the position, corresponding to the first small hole 11, of the right end of the central shaft 6, cylindrical pins are arranged in the first small hole 11 and the second small hole 15, and the central shaft 6 and the inner shell lining 4 are connected together through the cylindrical pins;
a cylindrical plunger 14 is arranged in the middle of the central shaft 6, turn-back threads 13 are respectively arranged on the central shaft 6 and positioned on the left side and the right side of the cylindrical plunger 14, and the turn-back threads 13 are composed of two threads with the same thread pitch and opposite rotation directions; crescent moon is arranged at the positions of the left piston 7 and the right piston 8 corresponding to the turn-back thread 13, the crescent moon is matched with the thread groove of the turn-back thread 13, and the initial positions of the left piston 7 and the right piston 8 are arranged at the leftmost end of the turn-back thread 13; the flow distribution cylinder 5 is driven by a high-speed motor to rotate, so that a left piston 7 and a right piston 8 are driven to rotate; when the piston rotates, the left piston 7 and the right piston 8 are subjected to the force of the return thread 13, so that the left piston 7, the flow distribution cylinder 5 and the right piston 8 are driven to perform axial reciprocating motion while rotating;
a left suction and discharge oil cavity 16 is formed by enclosing the left piston 7, the flow distribution cylinder body 5 and the cylindrical plunger 14, and a right suction and discharge oil cavity 17 is formed by enclosing the cylindrical plunger 14, the flow distribution cylinder body 5 and the right piston 8; the left suction and discharge oil cavity 16 and the right suction and discharge oil cavity 17 change along with the axial reciprocating motion of the left piston 7, the flow distribution cylinder 5 and the right piston 8; when the left piston 7, the distribution cylinder 5 and the right piston 8 move from the leftmost end to the rightmost end, the volume of the left suction and discharge oil chamber 16 is gradually reduced, and the volume of the right suction and discharge oil chamber 17 is gradually increased; conversely, when the left piston 7, the distribution cylinder 5 and the right piston 8 move from the rightmost end to the leftmost end, the volume of the right suction-discharge oil chamber 17 gradually decreases, and the volume of the left suction-discharge oil chamber 16 gradually increases;
the left rectangular groove and the right rectangular groove on the flow distribution cylinder body 5 are respectively communicated with the first waist-shaped oil port 10a and the second waist-shaped oil port 10b on the inner shell liner 4, an oil cavity with gradually increased volume absorbs oil, and the oil cavity with gradually decreased volume discharges oil.
The working principle is as follows:
the high-speed motor is connected with a left piston connecting shaft through a coupler to drive the flow distribution cylinder body 5, the left piston 7 and the right piston 8 to rotate, the left piston 7 and the right piston 8 can generate axial reciprocating motion under the action of the return thread 13 in the rotating process, the rotating angle is 0 degree when the left piston 7 and the right piston 8 start to move, the left piston 7 and the right piston 8 are positioned at the leftmost end, the left suction and discharge oil cavity 16 is positioned at the maximum volume, the right suction and discharge oil cavity 17 is positioned at the minimum volume, and the window of the flow distribution cylinder body 5 is not communicated with the suction and discharge oil port of the inner shell lining 4; when the rotation angle is rotated to 360 degrees/2 n from 0 degree, the window of the distribution cylinder body 5 is communicated with the oil port of the pump shell, the left piston 8 and the right piston 8 start to move rightwards, the volume of the left oil suction and discharge cavity 16 is reduced, oil is discharged from the oil discharge port, the volume of the right oil suction and discharge cavity 17 is increased, and oil suction is started; when the cylinder rotates to 360 degrees/2 n, the volumes of the left cavity and the right cavity are equal, and the window of the flow distribution cylinder body 5 is completely communicated with the oil port of the inner shell lining 4; when the rotation angle is from 360 degrees/2 n to 360 degrees/n, the piston continues to move rightwards, the left oil suction and discharge cavity 16 continues to discharge oil, the right oil suction and discharge cavity 17 continues to suck oil, and the window of the flow distribution cylinder body 5 is communicated with the oil port of the inner shell lining 4 from complete communication to non-communication; when the rotation angle is from 360 degrees/n to 3 degrees (360 degrees/2 n), the window of the flow distribution cylinder body 5 is communicated with the oil port of the inner shell lining 4, the piston starts to move leftwards, the left oil suction and discharge cavity 16 starts to suck oil, the right oil suction and discharge cavity 17 starts to discharge oil, when the piston rotates to 3 degrees (360 degrees/2 n), the volumes of the left cavity and the right cavity are equal, and the window of the flow distribution cylinder body 5 is completely communicated with the oil port of the inner shell lining 4; when the rotation angle is from 3X (360 degrees/2 n) to 4X (360 degrees/2 n), the piston continues to move leftwards, the left oil suction and discharge cavity 16 continues to suck oil, the right oil suction and discharge cavity 17 continues to discharge oil, when the piston rotates to 4X (360 degrees/2 n), the volume of the left oil suction and discharge cavity 16 reaches the maximum, and the window of the flow distribution cylinder body 5 is communicated with the oil port of the inner shell lining 4 from complete communication to non-communication; thus, one oil sucking and discharging period is completed, so that when the oil sucking and discharging device rotates for one circle, oil sucking and discharging can be performed for n/2 times, and the oil discharging amount is greatly increased.
The embodiments described in this specification are merely illustrative of implementations of the inventive concept and the scope of the present invention should not be considered limited to the specific forms set forth in the embodiments but rather by the equivalents thereof as may occur to those skilled in the art upon consideration of the present inventive concept.
Claims (2)
1. The spiral reciprocating hydraulic piston pump is characterized in that: the novel multifunctional electric heating cooker comprises an outer shell (1), wherein the left end and the right end of the outer shell (1) are respectively connected with a left end cover (2) and a right end cover (3), and coaxial shaft holes are formed in the left end cover (2) and the right end cover (3); an oil suction port is arranged on the left side of the outer wall of the outer shell (1), and an oil discharge port is arranged on the right side of the outer wall of the outer shell (1); the left end cover (2), the outer shell (1) and the right end cover (3) jointly enclose a pump cavity, and an inner shell lining (4) is arranged in the pump cavity;
the middle part of the outer wall of the inner shell lining (4) is provided with a step, and the step divides the outer wall of the inner shell lining (4) into a left section and a right section; a groove (9) is formed in the step, and an O-shaped ring is arranged in the groove (9) and used for separating oil liquid of the left section and the right section; the left section and the right section of the inner shell lining (4) are respectively provided with n/2 first waist-shaped oil ports (10a) and n/2 second waist-shaped oil ports (10b), the first waist-shaped oil ports (10a) are communicated with the oil suction port, and the second waist-shaped oil ports (10b) are communicated with the oil discharge port; the first waist-shaped oil port (10a) and the second waist-shaped oil port (10b) are uniformly distributed along the circumferential direction and are arranged in a staggered manner, and oil enters or is discharged through the first waist-shaped oil port (10a) and the second waist-shaped oil port (10 b); the right end of the right section of the inner shell lining (4) is provided with a first small hole (11) which is fixedly connected with the central shaft;
a left piston (7) and a right piston (8) of a flow distribution cylinder body (5) are arranged in the inner shell lining (4), n rectangular grooves (12) are uniformly distributed on the flow distribution cylinder body (5) along the circumferential direction, the rectangular grooves (12) are divided into a left rectangular groove and a right rectangular groove, a left through hole is formed in the bottom of the left side groove of the left rectangular groove, and a right through hole is formed in the bottom of the right side groove of the right rectangular groove; the left rectangular grooves and the right rectangular grooves are arranged in a staggered manner and are respectively communicated with the suction and discharge oil cavities (16) and the right suction and discharge oil cavities (17); the left end and the right end in the flow distribution cylinder body (5) are respectively connected with a left piston (7) and a right piston (8), the left piston (7) and the right piston (8) are in interference fit with the flow distribution cylinder body (5), and the left piston (7) is connected with a high-speed motor through a coupler;
a central shaft (6) is arranged in the left piston (7), the flow distribution cylinder body (5) and the right piston (8), and two ends of the central shaft (6) are respectively arranged in shaft holes of the left end cover (2) and the right end cover (3); a second small hole (15) is formed in the position, corresponding to the first small hole (11), of the right end of the central shaft (6), cylindrical pins are arranged in the first small hole (11) and the second small hole (15), and the central shaft (6) and the inner shell lining (4) are connected together through the cylindrical pins;
a cylindrical plunger (14) is arranged in the middle of the central shaft (6), turn-back threads (13) are respectively arranged on the central shaft (6) and positioned on the left side and the right side of the cylindrical plunger (14), and the turn-back threads (13) are formed by overlapping two threads with opposite rotation directions; crescent moon is arranged at the positions of the left piston (7) and the right piston (8) corresponding to the turn-back thread (13), and the crescent moon is matched with the thread groove of the turn-back thread (13); the flow distribution cylinder body (5) is driven by a high-speed motor to rotate, so that a left piston (7) and a right piston (8) are driven to rotate; when the piston is rotated, the left piston (7) and the right piston (8) are subjected to the force of the return thread (13), so that the left piston (7), the flow distribution cylinder body (5) and the right piston (8) are driven to perform axial reciprocating motion while rotating;
a left suction and discharge oil cavity (16) is enclosed among the left piston (7), the flow distribution cylinder body (5) and the cylindrical plunger (14), and a right suction and discharge oil cavity (17) is enclosed among the cylindrical plunger (14), the flow distribution cylinder body (5) and the right piston (8); the left suction and discharge oil cavity (16) and the right suction and discharge oil cavity (17) change along with the axial reciprocating motion of the left piston (7), the flow distribution cylinder body (5) and the right piston (8); when the left piston (7), the flow distribution cylinder body (5) and the right piston (8) move from the leftmost end to the rightmost end, the volume of the left suction and discharge oil cavity (16) is gradually reduced, and the volume of the right suction and discharge oil cavity (17) is gradually increased; on the contrary, when the left piston (7), the distribution cylinder body (5) and the right piston (8) move from the rightmost end to the leftmost end, the volume of the right suction and discharge oil cavity (17) is gradually reduced, and the volume of the left suction and discharge oil cavity (16) is gradually increased;
the left rectangular groove and the right rectangular groove on the flow distribution cylinder body (5) are respectively communicated with the first waist-shaped oil port (10a) and the second waist-shaped oil port (10b) on the inner shell lining (4), the oil cavity with gradually increased volume absorbs oil, and the oil cavity with gradually decreased volume discharges oil.
2. A spiral reciprocating hydraulic piston pump as set forth in claim 1, wherein: the angle between the n rectangular grooves (12) is 360 degrees/n, and the opening degree of the rectangular grooves is 360 degrees/2 n.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114876755A (en) * | 2022-05-16 | 2022-08-09 | 浙江工业大学 | Spiral reciprocating single-action plunger pump |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2083171A1 (en) * | 2008-01-25 | 2009-07-29 | Sigma Control S.r.l. | Fluid handling apparatus |
| JP2010514971A (en) * | 2006-12-29 | 2010-05-06 | ロバート ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング | Axial piston engine with housing gradually expanding inside |
| CN107989767A (en) * | 2017-12-11 | 2018-05-04 | 江苏精工泵业有限公司 | A kind of motor-direct-drive type ball-screw-transmission reciprocating pump |
| US20190145386A1 (en) * | 2017-11-10 | 2019-05-16 | Anhui University of Science and Technology | Magnetic piston shoe pair for axial piston pump and motor and control method thereof |
| CN210106086U (en) * | 2019-01-31 | 2020-02-21 | 浙江工业大学 | Heavy-duty force-balanced two-dimensional piston unit pump |
| CN111255917A (en) * | 2020-02-04 | 2020-06-09 | 宁波文泽机电技术开发有限公司 | Natural gas compressor control device |
-
2021
- 2021-12-13 CN CN202111520160.5A patent/CN114198276B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010514971A (en) * | 2006-12-29 | 2010-05-06 | ロバート ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング | Axial piston engine with housing gradually expanding inside |
| EP2083171A1 (en) * | 2008-01-25 | 2009-07-29 | Sigma Control S.r.l. | Fluid handling apparatus |
| US20190145386A1 (en) * | 2017-11-10 | 2019-05-16 | Anhui University of Science and Technology | Magnetic piston shoe pair for axial piston pump and motor and control method thereof |
| CN107989767A (en) * | 2017-12-11 | 2018-05-04 | 江苏精工泵业有限公司 | A kind of motor-direct-drive type ball-screw-transmission reciprocating pump |
| CN210106086U (en) * | 2019-01-31 | 2020-02-21 | 浙江工业大学 | Heavy-duty force-balanced two-dimensional piston unit pump |
| CN111255917A (en) * | 2020-02-04 | 2020-06-09 | 宁波文泽机电技术开发有限公司 | Natural gas compressor control device |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114876755A (en) * | 2022-05-16 | 2022-08-09 | 浙江工业大学 | Spiral reciprocating single-action plunger pump |
| CN114876755B (en) * | 2022-05-16 | 2024-06-07 | 浙江工业大学 | Screw reciprocating single acting piston pump |
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| CN114198276B (en) | 2023-03-31 |
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