WO2013127182A1 - 滑片泵和利用滑片泵输送流体的方法 - Google Patents

滑片泵和利用滑片泵输送流体的方法 Download PDF

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Publication number
WO2013127182A1
WO2013127182A1 PCT/CN2012/083306 CN2012083306W WO2013127182A1 WO 2013127182 A1 WO2013127182 A1 WO 2013127182A1 CN 2012083306 W CN2012083306 W CN 2012083306W WO 2013127182 A1 WO2013127182 A1 WO 2013127182A1
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WIPO (PCT)
Prior art keywords
pump
fluid
casing
vane
vane pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2012/083306
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English (en)
French (fr)
Inventor
郝忠献
沈泽俊
裴晓含
王全斌
王同斌
张立新
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Petrochina Co Ltd
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Petrochina Co Ltd
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Publication date
Application filed by Petrochina Co Ltd filed Critical Petrochina Co Ltd
Publication of WO2013127182A1 publication Critical patent/WO2013127182A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04C2/3441—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2/3446—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 the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C2240/00—Components
    • F04C2240/70—Use of multiplicity of similar components; Modular construction

Definitions

  • This invention relates to the field of hydraulics and, in particular, to a vane pump and a method of delivering fluid using a vane pump. Background technique
  • Slide pump A commonly used positive displacement pump, widely used in the industrial field of gathering and lifting, it has a strong self-priming capacity, especially suitable for oil ship dock unloading, onboard cargo, sweeping, train unloading Such occasions, as well as tank trucks, fuel trucks and oil depots, gas station oil delivery.
  • the vane pump can be used to transport light oil with better viscous oil.
  • Ordinary single-acting slide The pump works as shown in Figure 1.
  • the general single-acting vane pump is mainly composed of the following parts: drive shaft 1, connecting key 2, rotor 3, sliding vane 4, also called vane, stator is also called pump casing 5.
  • a drive shaft disposed in the pump casing, a rotor sleeved on the drive shaft and fixedly coupled to the drive shaft, a sliding piece extending laterally from the rotor and located at the rotor and the pump Between the shells.
  • the motor or other prime mover rotates the drive shaft 1
  • the drive shaft 1 rotates the rotor 3 through the key 2
  • the rotor 3 drives the slide 4 to rotate in the eccentric chamber of the pump casing 5, and the blade 4 is driven by the centrifugal force and the stator cavity.
  • the contact seal because the vane 4 and the stator 5 constitute a volume change of the chamber, allows the vane pump to pump and squeeze the fluid.
  • the contour of the inner cavity of the stator or the pump casing 5 is modified to a symmetrical elliptical shape or an approximately elliptical shape, and the contour line can be a plurality of curve equations, and the suction port is provided at the stator or the pump casing 5 There are two outlets and two outlets. Usually, the circumferential angle of the suction port and the discharge port is 90°.
  • This is the commonly used double-acting vane pump, as shown in Figure 2.
  • the drive shaft rotates once, and the double-acting slide pump draws in and out twice.
  • double-acting vane pumps tend to achieve greater displacement due to the symmetrical structure and load, while reducing the noise of the vane pump and improving the reliability of the drive shaft and other components.
  • Figure 3 shows the basic three-dimensional structure of a conventional single-acting vane pump. It mainly consists of the following parts: drive shaft 1, end cover 6, stator or pump casing 5, rotor 3 and slide 4.
  • the slide pumps commonly used in the above-mentioned industries are used separately in operation, that is, the conveying medium is sucked from the low pressure end, discharged from the high pressure end, the suction port and the discharge port. They are all disposed laterally of the stator (or pump casing) in the form of a radial suction and discharge bypass structure, for example, Japanese Patent JP1-177478A, and Chinese patent CN2379622Y, both of which are used for radial suction and discharge.
  • the general structure makes the direction of suction and discharge often perpendicular to the rotating shaft of the vane pump.
  • the radial size of the vane pump is increased, resulting in a larger volume of the vane pump.
  • the bypass structure requires a large radial dimension to achieve lift fluids (eg, lift oil) displacement and pressure that cannot be installed in a limited size casing.
  • the above-mentioned conventional vane pump adopts a bypass structure of radial suction and discharge, and if it is to be lowered into the oil well for lifting crude oil, it will be set in the radial direction during the process of descending to the oil well.
  • the pipeline will be damaged, it is difficult to install safely and stably under the well, and the radially installed suction and discharge pipelines are difficult to withstand the huge pressure and corrosion under the well, and cannot work under the condition of crude oil flooding, so the radial suction and discharge
  • the bypass structure limits the application of the vane pump to downhole lift.
  • the invention provides a sliding vane pump and a method for transporting fluid by using a vane pump, so as to solve the problem that the radial diameter of the conventional vane pump is large, the vane pump is large in volume, and it is difficult to adapt to a narrow tubular space. Further, the present invention can solve the problem that the pumping pressure of the vane pump is small.
  • the present invention provides a vane pump having a cylindrical pump casing, the pump casing being provided with: a drive shaft, a rotor sleeved on the drive shaft, and a rotor disposed on the rotor a sliding piece, the sliding piece is in contact with the inner cavity of the pump casing, the end of the pump casing is provided with an end cover, and the sliding plate pump further has a sliding plate pump suction port and a sliding plate pump discharge port The slide pump suction port and/or the vane pump discharge port are located on an end cover of the pump casing.
  • the slide pump suction port and the vane pump discharge port are both one, and in the circumferential direction, the vane pump suction port and the vane pump discharge port are symmetrically disposed with respect to the drive shaft.
  • the end cover includes: a bottom cover and a top cover located above the bottom cover, the sliding plate pump suction port is disposed on the bottom cover, and the sliding plate pump discharge port is disposed on the top cover on.
  • the slide pump suction port includes: a first suction port and a second suction port disposed on the bottom cover
  • the slide pump discharge port includes: a first row disposed on the top cover An outlet and a second discharge port, wherein a line connecting the first suction port and the second suction port to an axis of the drive shaft is a straight line, and the first discharge port and the second discharge port are connected to the drive shaft
  • the line connecting the axes is a straight line
  • the line connecting the first suction port and the second suction port is perpendicular to the line connecting the first discharge port and the second discharge port.
  • the present invention also provides a vane pump having a passage for conveying fluid from bottom to top, the vane pump comprising a plurality of cylindrical pump casings, a plurality of the pump casings from the head end to the tail end
  • the vane pump comprising a plurality of cylindrical pump casings, a plurality of the pump casings from the head end to the tail end
  • the ends of the ends are connected in sequence, the driving shaft passes through the inner cavity of each of the pump casings, and the pump casings are sleeved on the driving shaft, and the plurality of pump casings at least include the pump casing and the tail end of the head end.
  • a pump casing, the sliding pump is provided with end caps at both ends thereof, one end cap is located at the head end of the pump casing at the head end, and the other end cap is located at the tail end of the pump casing at the tail end;
  • the slide pump is provided with n partitions sleeved on the drive shaft, n is equal to or equal to 1, and the partition plate separates two adjacent pump casings, and each pump casing is a rotor is disposed on the driving shaft, and a rotor is disposed on the rotor, and the sliding piece is in contact with the inner cavity of the pump casing;
  • the vane pump further has a vane pump suction port and a vane pump discharge port, and the vane pump suction port and/or the vane pump discharge port are respectively located on the end cover, and the partition plates are Each of which is provided with a fluid transfer opening extending through the upper and lower end faces of the respective partitions, the passage for conveying the fluid passes through the slide pump suction port, the fluid transfer opening and the vane pump discharge port, and the passage for conveying the fluid is located in each of the In the inner cavity of the pump casing.
  • the end cover includes: a bottom cover and a top cover located above the bottom cover, the sliding plate pump suction port is disposed on the bottom cover, and the sliding plate pump discharge port is disposed on the top cover
  • the plane of each of the partitions is perpendicular to the drive shaft, except for the pump casings at both ends, and in each of the other pump casings, the fluid transfer opening of the lower baffle is the suction port of the pump casing, and the fluid of the upper baffle
  • the transfer opening is a discharge port of the pump casing; the slide pump suction port, the slide pump discharge port, and the number of fluid transfer openings on each of the baffles are one, and in the circumferential direction, the vane pump is sucked
  • the port and the adjacent fluid transfer opening, the adjacent two fluid transfer openings or the vane pump discharge port and the adjacent fluid transfer opening are symmetrically arranged with respect to the drive shaft, and the inner cavities of each pump casing are all eccentric in shape In the chamber, in the circumferential direction, the two pump
  • the end cover includes: a bottom cover and a top cover located above the bottom cover, the sliding plate pump suction port is disposed on the bottom cover, and the sliding plate pump discharge port is disposed on the top cover
  • the plane in which each of the partition plates is located is perpendicular to the drive shaft, and the fluid transfer opening of the lower partition plate is the suction port of the pump casing in each pump casing, and the fluid transfer opening of the upper partition plate is the row of the pump casing
  • the number of fluid transfer openings of the sliding plate pump suction port, the sliding plate pump discharge port and each of the partition plates is two, and the circumferential interval angle between the two sliding plate pump suction ports is 180 degrees.
  • the circumferential spacing angle between the two slide pump discharge ports is 180 degrees, and the circumferential spacing angles of the two fluid transfer openings on the same partition plate are 180 degrees; the sliding plate pump suction port is adjacent to the adjacent
  • the circumferentially spaced angle of the fluid transfer opening of the baffle of the bottom cover is 90 degrees, and/or the circumferential spacing angle of the fluid transfer opening of the upper and lower adjacent baffles is 90 degrees, and/or the slide pump discharge port
  • the circumferential direction of the fluid transfer opening with the partition of the adjacent top cover Interval angle of 90 degrees, each of the lumen of the pump housing are of the same shape eccentric chamber in the circumferential direction, the vertical direction is provided adjacent to the pump housing two mutually perpendicular.
  • the slide pump is provided with a partition sleeve disposed on the drive shaft, wherein a plane of the partition plate is perpendicular to the drive shaft, and the one partition plate pumps the slide plate
  • the two pump casings are arranged one above the other, which are respectively an upper pump casing and a lower pump casing, and each of the pump casings is provided with a rotor sleeved on the drive shaft, and the rotor passes through a connecting rod is fixedly connected to the driving shaft, the rotor is provided with a sliding piece, and the sliding piece is in contact with the inner cavity of the pump casing;
  • the end cover comprises: a bottom cover and a bottom cover a top cover, the sliding plate pump suction port is disposed on the bottom cover, the sliding plate pump discharge port is disposed on the top cover, and the one baffle is provided with fluid transfer through the upper and lower end faces of the baffle
  • the opening, the fluid transfer opening is a discharge port of the lower pump casing, and is also a
  • the number of fluid transfer openings of the slide pump suction port, the sliding plate pump discharge port and one of the partition plates is one, and in the circumferential direction, the sliding plate pump suction port and a station
  • the fluid transfer opening on the partition plate, the slide pump discharge port and the fluid transfer opening on one of the partition plates are symmetrically arranged with respect to the drive shaft, and the upper pump casing and the lower pump casing have the same shape.
  • the upper pump casing and the lower pump casing are disposed at an angle of 180 degrees.
  • the number of fluid transfer openings of the slide pump suction port, the slide pump discharge port, and the one partition plate are two, and the circumferential intervals of the suction ports of the two slide pumps are The angle is 180 degrees, the circumferential spacing angle of the two pump discharge ports is 180 degrees, and the circumferential spacing angle of the two fluid transfer openings on the one partition is 180 degrees; the slide pump suction The circumferential gap of the fluid transfer opening of the one partition of the port is 90 degrees, and the circumferential distance between the slide pump discharge port and the fluid transfer opening of the one partition is 90 degrees, and the upper pump casing and The inner chambers of the lower pump casing are all eccentric chambers of the same shape. In the circumferential direction, the upper pump casing and the lower pump casing are disposed at an angle of 90 degrees.
  • the vane pump comprises two cylindrical pump casings which are sequentially connected, and the vane pump is provided with a partition plate which is sleeved on the drive shaft.
  • the sliding vane pump comprises three cylindrical pump casings which are sequentially connected, and the sliding vane pump is provided with two partition plates which are sequentially sleeved on the driving shaft.
  • the present invention also provides a method for transporting fluid using a vane pump, the vane pump having a cylindrical pump casing, the pump casing being provided with a drive shaft, and the method of transporting fluid by the vane pump from the The end of the pump casing is drawn in and/or discharged for pumping.
  • the slide pump is divided into a plurality of pump casings arranged one above another in sequence, and the plurality of pump casings are sequentially connected in a direction from the head end to the tail end, and each pump casing is adopted from the pump casing.
  • the fluid is sucked and discharged in the end direction, the fluid is transported from bottom to top, the fluid is sucked in by the lowermost pump casing, and is pumped out by the uppermost pump casing, wherein the adjacent two pump casings are separated by the partition plate.
  • the separator is provided with a fluid transfer opening penetrating through the upper and lower end faces of the partition plate, and the fluid passes through the slide pump suction port, the fluid transfer opening and the slide pump discharge port, and the fluid discharged from the lower pump casing passes through the fluid transfer opening.
  • the fluid sucked from the upper end of the pump casing is sucked in by the upper pump casing to form a suction and discharge relay until the sucked fluid is pumped out by the uppermost pump casing.
  • the direction of the suction and/or discharge fluid is parallel to the axial direction of the drive shaft.
  • the slide pump is divided into a plurality of pump casings, and the plurality of pump casings are sequentially connected in a direction from a head end to a tail end, and the plurality of pump casings at least include a pump casing at a lowermost head end and The pump casing at the uppermost end, the fluid is transported from bottom to top, the fluid is sucked in by the lowermost pump casing, and is pumped out by the uppermost pump casing.
  • the pump casing at the head end discharges fluid from the upper end, and the pump casing at the tail end is from the lower end.
  • each of the pump casings draws and discharges fluid from the end of the pump casing, including the pump casing at the head end and the pump casing at the end.
  • the fluid discharged from the lower pump casing is sucked by the upper pump casing, and the fluid sucked by the upper pump casing is sucked by the upper pump casing to form a suction and discharge relay until The inhaled fluid is pumped out by the uppermost pump casing.
  • the direction of the suction and/or discharge fluid is parallel to the axial direction of the drive shaft.
  • the invention draws in and/or discharges fluid from the end of the pump casing, and the volume of the cavity formed by the blade and the pump casing is continuously changed by the rotation of the rotor, forming a suction pump inlet and a pump casing.
  • the low pressure chamber communicates, and the vane pump discharge port communicates with the high pressure chamber, which generates a pressure difference between the vane pump suction port and the vane pump discharge port, thereby realizing pumping of the fluid.
  • the present invention draws in and/or discharges fluid from the end of the pump casing.
  • the invention also realizes the change of the potential energy of the fluid, and when the suction port of the vane pump and the discharge port of the vane pump are arranged at the end of the pump casing, the influence of the vane pump on the change of the fluid potential energy is maximized, especially The potential energy is increased, which is different from the traditional sliding plate pump suction port and the sliding plate pump discharge port in the lateral direction of the pump casing, and the height difference between the sliding plate pump suction port and the vane pump discharge port is not obvious, and the fluid potential energy cannot be affected.
  • the vane pump not only has the function of supercharging or pumping, but also makes the vane pump have a higher lifting capacity, so that the vane pump is not limited to the oil tanker unloading oil, the cargo oil on board, Sweeping cabins, train unloading and other occasions, as well as tank trucks, fuel trucks and oil depots, gas station oil delivery, can also be used in applications where lifting is required.
  • the invention avoids the suction and discharge of fluid from the lateral direction of the pump casing, reduces the radial size and radial volume of the vane pump, can adapt to the narrow tubular space, and increases the application range of the vane pump. Since the passage for conveying fluid of the present invention is located in the inner cavity of the pump casing, there is no need to provide a radially disposed suction and discharge line of the prior art, so the present invention overcomes the existing bypass pump of the conventional type due to Radially arranged suction and discharge lines make it difficult to safely and stably install in the well, it is difficult to withstand the pressure and corrosion of the underground and can not work under the conditions of crude oil flooding, so that the protection of the pump casing or pump cylinder makes it
  • the slide pump realizes comprehensive improvement of sand resistance, gas resistance, corrosion resistance and pressure resistance while achieving lifting and pressurization, and can work under the condition of crude oil flooding, achieving 24 hours of unattended duty.
  • the passage for conveying fluid of the present invention is located in the inner cavity of each of the cylindrical stators, and the liquid is transported with respect to the suction and discharge lines radially disposed of the conventional bypass pump.
  • the transportation of liquid to the radially disposed suction and discharge lines by centrifugation is avoided, the loss of liquid transport efficiency is reduced, and the flow rate and pressure of the transport are increased by internal transport, especially axial transport, and
  • the present invention shortens the path of liquid delivery, further reduces liquid transmission losses, and reduces the loss of pressure and flow rate of the liquid in the radial direction.
  • the direction of suction and discharge of the present invention is substantially straight or the direction of suction and discharge of fluid is axial, and the loss of velocity and efficiency is small, whereas the suction and discharge of the prior art are bypassed, and the fluid is sucked in and discharged. A large shift occurs in the direction, so that the technical by-product suction and discharge produces more loss of speed and loss of efficiency.
  • the invention also realizes the relay pressurization of the multi-stage vane pump by using a plurality of pump casings arranged in the upper and lower rows in sequence, thereby utilizing the suction and discharge of the pumping fluid from the end direction, so as to further adapt to the fluid in the tube cylinder.
  • Conveying and lifting operations can greatly improve the lifting capacity of the vane pump, so that the vane pump can be applied to the restricted area of traditional vane pump applications, such as lifting of fluids, including oil extraction, expanding the application range of vane pumps. . DRAWINGS
  • FIG. 1 is a schematic diagram showing the working principle of the conventional single-acting vane pump
  • Figure 2 is a schematic view showing the working principle of the existing double-acting vane pump
  • Figure 3 shows the three-dimensional structure of the single-acting vane pump in a cross-sectional view
  • FIG. 4 is a schematic exploded view of a single-stage single-acting axial flow type slide pump according to an embodiment of the present invention
  • Figure 5 is a cross-sectional view showing a three-dimensional exploded structure of a single-stage single-acting axial flow type slide pump according to an embodiment of the present invention
  • Figure 6 is a cross-sectional view showing a three-dimensional combination structure of a single-stage single-acting axial flow type slide pump according to an embodiment of the present invention
  • FIG. 7 is a schematic exploded view of a two-stage single-acting axial flow type slide pump according to an embodiment of the present invention.
  • Figure 8 is a cross-sectional view showing a three-dimensional combination structure of a two-stage single-acting axial flow type slide pump according to an embodiment of the present invention
  • FIG. 9 is a perspective assembled structure of a two-stage single-acting axial flow type slide pump according to an embodiment of the present invention
  • FIG. 10 is an exploded perspective view of a single-stage double-acting axial flow type slide pump according to an embodiment of the present invention
  • Figure 11 is a cross-sectional view showing a three-dimensional decomposition of a single-stage double-acting axial flow type slide pump according to an embodiment of the present invention. Structure
  • Figure 12 is a cross-sectional view showing the three-dimensional exploded structure of a two-stage double-acting axial flow type slide pump according to an embodiment of the present invention
  • Figure 13 is a cross-sectional view showing a three-dimensional combination of a two-stage double-acting axial flow type slide pump according to an embodiment of the present invention.
  • the present invention provides a vane pump, which has a cylindrical pump casing 5, and the pump casing 5 is provided with: a drive shaft 1 and a drive shaft.
  • the upper rotor 3, the rotor 3 is fixedly connected to the drive shaft 1 via a connecting key 2, and is disposed on the rotor 3, and the sliding plate 4 is in contact with the inner cavity of the pump casing 5, the pump An end cap is provided at an end of the casing 5, the vane pump further has a vane pump suction port 70 and a vane pump discharge port 80, the vane pump suction port 70 and/or the vane pump discharge port 80 Located on the end cover of the pump casing, the sliding plate pump suction port 70 and the vane pump discharge port 80 are located on the end cover of the pump casing for the sake of compactness, and the sliding is maximized.
  • the pump has potential energy to the fluid.
  • the slide pump suction port 70 or the vane pump discharge port 80 can also increase the fluid potential energy function as long as it has a fluid from the end direction, and the other can still be disposed in the lateral direction of the pump casing.
  • the radial dimension of the vane pump in the area is only that the vane pump suction port 70 and the vane pump discharge port 80 are simultaneously disposed on the end cover of the pump casing, so that the radial size of the vane pump can be better minimized. It can maximize the potential energy of the fluid.
  • the vane pump suction port 70 and the vane pump discharge port 80 are located on the end cover of the pump casing,
  • the shape of the pump casing 5 in the vane pump, the shape of the drive shaft 1, the vane pump suction port 70, the shaft end seal of the vane pump of the vane pump discharge port 80, and the bearing support, the end cover of the pump casing 5 The shape and the connection relationship of the above components in the vane pump, as well as the working principle of low pressure suction and high pressure discharge are not the focus of the present invention.
  • the above structure and working principle can be referred to and adopt a suitable structure of various conventional vane pumps.
  • the vane pump suction port is connected or in communication with the low pressure chamber of the pump casing
  • the vane pump discharge port is connected or communicated with the high pressure chamber of the pump casing.
  • the end cover includes: a bottom cover 63 and a top cover 61 located above the bottom cover, each of the end covers being The disk shape is provided with a shaft hole through which the drive shaft 1 passes, and the plane of each of the end covers is perpendicular to the drive shaft 1, which facilitates the rotation of the drive shaft 1. Further, the vane pump suction port 70 is disposed on the bottom cover 63, and the vane pump discharge port 80 is disposed on the top cover 61.
  • the vane pump suction port 70 and the vane pump discharge port 80 are through holes respectively penetrating the bottom cover 63 and the top cover 61, and the vane pump suction port and the vane pump discharge port are both one in the circumferential direction.
  • the slide pump suction port and the vane pump discharge port are symmetrically disposed with respect to the drive shaft, and the vane pump suction port 70 and the vane pump discharge port 80 may have a long arc shape, and may of course be other shape.
  • the vane pump of the present invention sucks in a low-pressure fluid from the bottom end of the vane pump suction port 70, and the volume of the fluid formed by the rotation of the vane pump rotor during the rotation of the rotor 3 causes the sucked in fluid and discharged A pressure difference is formed between the fluids, and the high pressure fluid is discharged from the vane pump discharge port 80 of the top cover 61.
  • the present invention fundamentally avoids the suction and discharge of fluid from the lateral side of the pump casing, reducing the vane pump.
  • the radial size and radial volume allow for a narrow tubular space and increase the range of applications for the vane pump.
  • the present invention is not limited to suction and discharge of fluid only from the end cap, as long as the fluid can be sucked and discharged from the end of the pump casing for pumping, regardless of whether or not the vane pump is provided with an end cap, regardless of whether the fluid passes or not.
  • the end cover, the invention can realize the end suction and discharge of the fluid.
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump of the present invention can also be called (also)
  • the slide pump suction port 170 includes: a first suction port and a second suction port disposed on the bottom cover 163 and the slide pump discharge port 180 includes: a first discharge port and a second discharge port on the top cover 161, the sliding plate pump suction port is connected or communicated with the low pressure chamber of the pump casing, and the sliding plate pump discharge port is connected or connected with the high pressure chamber of the pump casing;
  • the first suction port and the first a line connecting the two suction ports to the axis of the drive shaft 1 is a straight line
  • a line connecting the first discharge port and the second discharge port to the axis of the drive shaft is a straight line
  • the first suction The line connecting the mouth and the second suction port is perpendicular to the line connecting the first discharge port and the second discharge port.
  • the circumferential distance between each of the sliding plate pump suction ports and each of the sliding plate pump discharge ports is 90 degrees, so that a larger displacement can be obtained, and the noise of the sliding plate pump can be reduced, and the components of the driving shaft and the like can be improved. reliability.
  • the connection of the rotor 3 to the drive shaft 1 through the connection key 2, and the structure in the pump casing 5 can be the same as that of the single-acting pump.
  • the present invention also provides a vane pump which is a two-stage single-acting axial flow vane pump.
  • the slide pump has two separate cylindrical pump casings 25, and each pump casing 25 is sequentially engaged and sleeved in a direction from the head end to the tail end, and each of the pump casings is provided with a drive shaft 21, a drive shaft 21 may be an integral shaft, the integral shaft passing through each pump casing 25, each of the pump casings being sleeved on the illustrated drive shaft, and the vane pump is provided with a partition sleeved on the drive shaft 21 a plate 22, the plane of the partition 22 is perpendicular to the drive shaft 21, and the partition 22 divides the slide pump into two pump casings arranged one above another;
  • Each of the pump casings is provided with a rotor 23 sleeved on the drive shaft, and the rotor 23 is fixedly connected to the drive shaft 21 via a connecting key, and the rotor is provided with a sliding piece, the sliding piece and the sliding plate
  • the inner casing of the pump casing is in contact with the seal; the end of the pump casing is provided with an end cover, and the end cover comprises: a bottom cover 263 and a top cover 261 located above the bottom cover, the slide pump suction port 270
  • the slide pump discharge port 280 is disposed on the top cover 263, and the partition plate 22 is provided with a fluid transfer opening 24 extending through the upper and lower end faces of the partition plate 22.
  • the partition 22 may have the same structure as each of the end caps, for example, both of which are disc-shaped.
  • the fluid transfer opening 24, the vane pump suction port 270, and the vane pump discharge port 280 may have the same shape and may be long curved.
  • the partition 22 can be replaced with each of the end caps to facilitate the installation.
  • each pump casing can be welded to the partition plate 22.
  • the lower pump casing and the components therein form a primary pump 100
  • the upper pump casing and the components therein form a secondary pump 200
  • the fluid transfer opening 24 is both the discharge port of the upper stage pump and the suction port of the next stage pump.
  • the stator of the two-stage axial flow vane pump (or the pump casing) is 180 ° opposite, thus achieving 180° opposition between the upper pump and the lower pump high pressure chamber and the low pressure chamber, that is,
  • the fluid transfer opening 24 is connected to the high pressure chamber of the primary pump 100, and is connected to the low pressure chamber of the secondary pump 200, so that the partition 22 between the two axial flow vane pumps can simultaneously serve as a discharge port (upper stage pump) The discharge port) and the suction port (the suction port of the next stage pump).
  • the drive shaft when the drive shaft rotates, the drive shaft simultaneously drives the rotor and vane movements of each stage, and the primary axial vane pump 100 passes through the suction port of the vane pump.
  • 270 takes in fluid and discharges fluid from the fluid transfer opening 24, and pressurizes the fluid into the suction end of the secondary axial flow vane pump 200.
  • the suction end of the secondary axial flow vane pump 200 is also a fluid transfer opening 24, which is also a At the discharge end of the stage axial flow vane pump 100, the secondary axial flow vane pump pressurizes the fluid and discharges it from the vane pump discharge port 280.
  • the overall pressure multiplier of the vane pump is squared by m after being pressurized by the two-stage axial flow vane pump. After three stages, the overall supercharging factor is cubic of m, and after n stages, The overall pressure multiplier of the vane pump is n-th power of m.
  • the partitions of the partitions 22 make the pump casings independent of each other, so that each pump casing can form a pumping of the fluid and a relay of the fluid transfer opening 24, so that the pumps
  • the suction and discharge of the shell are interrelated and form a relay pressurization of the multi-stage vane pump.
  • the relay pressurization of the multi-stage vane pump can be realized by the separation of the partition 22 and the relay of the fluid transfer opening 24 in the interior of the vane pump, as for the vane pump suction port and the vane pump discharge port.
  • the vane pump suction port and the vane pump discharge port may both be disposed laterally of the vane pump, or in the vane pump suction port and the vane pump discharge port One is disposed at the end of the vane pump, and the other is disposed at the lateral direction of the vane pump, except that the vane pump suction port and the vane pump discharge port are disposed at the end of the vane pump to save space. It is also easy to process.
  • the slide pump of the present invention is not limited to the two-stage pump, and may be a multi-stage pump.
  • the vane pump includes three or more cylindrical pump casings, and the plurality of pump casings are sequentially connected in a direction from the head end to the tail end, and the drive shaft passes through the inner cavity of each of the pump casings.
  • the plurality of pump casings at least include a pump casing of the head end and a pump casing of the tail end, the end of the sliding plate pump is provided with an end cap, one end cap is located at the head end of the pump casing at the head end, and the other end cap is located at the tail end a tail end of the pump casing;
  • the slide pump is provided with two or more partitions sleeved on the drive shaft, the partition separating two adjacent pump casings, each
  • the pump casing is provided with a rotor sleeved on the drive shaft, and a rotor is disposed on the rotor, the sliding piece is in contact with the inner cavity of the pump casing;
  • the sliding plate pump further has a sliding plate pump suction port.
  • a slide pump discharge port, the slide pump suction port and/or the slide pump discharge port are respectively located on the end cover, and each of the partition plates is provided with an upper and lower end surface of each of the partition plates Fluid transfer opening.
  • each pump casing can be constructed and functiond identically or similarly to the structure and function of the two-stage pump, using partitions to separate the pumps.
  • the shells are independent of each other, so that each pump casing can form a pumping of the fluid and a transit of the fluid transfer opening, so that the suction and discharge of the pump casings are related to each other, forming a relay pressurization of the multi-stage vane pump.
  • the pump housing at the head end and the pump housing at the end are identical in construction to the upper pump housing and the lower pump housing in the two-stage vane pump, with three stages.
  • the slide pump of the multi-stage pump also has a pump casing located between the ends of the first and last ends, and the pump casing in the middle is a primary pump surrounded by upper and lower partitions, and the fluid transfer opening on the partition Still functioning as a fluid transfer, that is, the fluid transfer opening is the discharge port of the lower pump casing, and is also the suction port of the upper pump casing, in which the fluid is sucked from the fluid transfer opening of the lower layer, The fluid transfer opening of the upper layer is discharged, and the initial suction fluid of the vane pump is still sucked from the suction port of the vane pump, and finally the discharge fluid is still discharged from the discharge port of the vane pump, and the fluid transfer opening is connected with the high pressure chamber of the lower stage pump. When connected to the low pressure chamber of the higher stage pump, the fluid is pressurized from the lower stage pump to the higher stage pump.
  • the vane pump is a two-stage double-acting vane pump.
  • the main difference between the two-stage double-acting vane pump and the two-stage single-acting vane pump is that the two-stage double-acting vane pump has more than one of the two-stage single-acting vane pump and one of the vane pump suction ports and one of the slides.
  • the vane pump suction port 370 is disposed on an upper end cover (also referred to as a top cover) 361, and the vane pump discharge port 380 is disposed on a lower end cover (also referred to as a bottom cover) 363.
  • the number of the slide pump suction port 370, the vane pump discharge port 380, and the fluid transfer opening 34 on the partition plate 32 are both two, and the circumferential direction of the two slide pump suction ports 370
  • the interval angle is 180 degrees
  • the circumferential spacing angle of the two sliding pump discharge ports 380 is 180 degrees
  • the circumferential spacing angle of the two fluid transfer openings 34 on the one partition plate is 180 degrees
  • the circumferential distance between the plate pump suction port 370 and the fluid transfer opening 34 of the partition plate 32 is 90 degrees
  • the circumferential distance between the slide pump discharge port 380 and the fluid transfer opening 34 of the partition plate 32 is 90 degrees.
  • the inner chambers of the pump casings 35 may each have an eccentric chamber of the same shape.
  • the two pump casings disposed adjacent to each other are perpendicular to each other, that is, the fluid transfer opening 34 and the high pressure chamber of the primary pump 3100. Connected to the low pressure chamber of the secondary pump 3200.
  • Other structures are the same as or similar to those of the two-stage single-acting vane pump.
  • the vane pump suction port 370 is disposed on the bottom cover 363
  • the vane pump discharge port 380 is disposed on the top cover 361.
  • the drive shaft 31 vertically passes through the partition plate 32, the bottom cover 363 and the top cover 361.
  • the drive shaft 31 is provided with a rotor 33 and blades, so that the partition between the two-stage axial flow vane pumps can simultaneously serve as a discharge port (on The discharge port of the primary pump) and the suction port (the suction port of the next stage pump). Fluid can be drawn into the primary pump 3100 from the two vane pump suction ports 370, and after being pressurized, is discharged from the two fluid transfer openings 34 into the secondary pump 3200, and the secondary pump 3200 transfers the openings 34 from the two fluids. The fluid discharged from the primary pump 3100 is pressurized and discharged from the vane pump discharge port 380.
  • the two vane pump discharge ports 380 which achieves multi-stage supercharging and achieves a larger fluid displacement, and at the same time reduces the noise of the vane pump and improves Reliability of components such as drive shafts.
  • the structure of the inner cavity and the rotor of each of the pump casings 35 is not limited to the eccentric chamber structure, and other types are also included.
  • a three-stage or more double-acting axial flow vane pump wherein the pump casing is provided with a partition sleeve disposed on the drive shaft, and a plane of the one partition plate is perpendicular to the drive shaft, a baffle divides the inner cavity of the pump casing into two pump casings arranged one above another, each of which is provided with a rotor sleeved on the drive shaft, the rotor being connected to the
  • the driving shaft is fixedly connected, the rotor is provided with a sliding piece, and the sliding piece is in contact with the inner cavity of the pump casing;
  • the end cover comprises: a bottom cover and a top cover located above the bottom cover, a slide pump suction port is disposed on the bottom cover, The slide pump discharge port is disposed on the top cover, and the one partition plate is provided with a fluid transfer opening penetrating the upper and lower end faces of the partition plate; the slide pump suction port, the slide pump discharge port, and The number of fluid transfer openings
  • the present invention also provides a method for transporting fluid using a vane pump, the vane pump having a cylindrical pump casing, the pump casing being provided with a drive shaft, and the method of transporting fluid by the vane pump from the The end of the pump casing draws in and discharges fluid for pumping.
  • the 13 adopts suction and discharge of fluid from the end of the pump casing for pumping, for example, from the upper end to the lower end, and
  • the lower end to the upper end conveyance show that the suction port and the discharge port are provided on the end cover, and the present invention is not limited to providing the suction port and the discharge port on the end cover to be from the end of the pump casing.
  • Inhalation and discharge of the fluid are carried out, and other fluids can be taken in and out from the end of the pump casing, for example, a pump casing not provided with an end cap is sucked and discharged from the end of the casing.
  • more single-stage and more-stage double-action can increase the number of pumping stages by increasing the pump casing, the diaphragm and the fluid transfer opening to achieve more stages of pumping.
  • the method of injecting and discharging fluid from the end of the pump casing for pumping in the present invention enables the upper pump casing to be sucked into the lower pump casing inside the vane pump between the adjacent two-stage pump casings.
  • the discharge realizes the zero distance conversion between the suction and discharge between the two-stage pump casing.
  • the present invention is not limited to sucking and discharging only fluid from the end cap, and the end cap of the present invention is not limited to a disk shape as long as it can perform suction and discharge of fluid from the end of the pump casing to perform pumping. Regardless of whether the vane pump is provided with an end cap, the present invention enables end suction and discharge of fluid regardless of whether the fluid passes through the end cap.
  • one of the vane pump suction port and the vane pump discharge port is disposed at the end of the vane pump, and the other may be disposed at the lateral direction of the vane pump, which also realizes space saving of the present invention.
  • the purpose is only that the sliding plate pump suction port and the sliding plate pump discharge port are disposed at the end of the sliding plate pump to save space and facilitate processing.
  • the relay pressurization of the multi-stage vane pump can be realized as long as the partition of the vane pump is separated by the partition and the transfer of the fluid transfer opening, as for the vane pump suction port and the vane pump
  • the discharge port may not be disposed at the end of the vane pump, for example, the vane pump suction port and the vane pump discharge port may both be disposed laterally of the vane pump, or the vane pump suction port and the vane pump One of the discharge ports is disposed at the end of the vane pump, and the other is disposed at the lateral direction of the vane pump.
  • the slide pump suction port and the vane pump discharge port are both disposed at the end of the vane pump to save space and facilitate processing.
  • the slide pump of the present invention has a more compact structure, a better conveying effect, and a more desirable radial dimension.
  • the slide pump is divided into a plurality of pump casings arranged one above another in sequence, and the plurality of pump casings are sequentially connected in a direction from the head end to the tail end, and each pump casing is adopted from the pump casing.
  • the fluid is sucked and discharged in the direction of the end, the fluid is transported from bottom to top, the fluid is sucked in by the lowermost pump casing, and is pumped out by the uppermost pump casing, wherein the lower pump casing is discharged from the adjacent two pump casings.
  • the fluid is drawn in by the upper pump casing, and the fluid sucked in the upper pump casing is sucked in by the upper pump casing to form a suction and discharge relay until the sucked fluid is pumped out by the uppermost casing.
  • the two-stage single-acting vane pump, the two-stage double-acting vane pump shown in Figures 12 to 13, the partition of the vane pump through the partition and the relay of the fluid transfer opening The relay pressurization of the multi-stage vane pump can be realized.
  • the method of setting a plurality of pump casings can realize the relay pressurization of the multi-stage vane pump, and the supercharging method greatly improves the supercharging effect of the vane pump and Lifting effect.
  • the slide pump is divided into a plurality of pump casings, and the plurality of pump casings are sequentially connected in a direction from a head end to a tail end, and the plurality of pump casings at least include a pump casing at a lowermost head end and The pump casing at the uppermost end, the fluid is transported from bottom to top, the fluid is sucked in by the lowermost pump casing, and is pumped out by the uppermost pump casing.
  • the pump casing at the head end discharges fluid from the upper end, and the pump casing at the tail end is from the lower end.
  • each of the pump casings draws and discharges fluid from the end of the pump casing, including the pump casing at the head end and the pump casing at the end.
  • the fluid discharged from the lower pump casing is sucked by the upper pump casing, and the fluid sucked by the upper pump casing is sucked by the upper pump casing to form a suction and discharge relay until The inhaled fluid is pumped out by the uppermost pump casing.
  • the pump casing of the head end and the pump casing of the tail end can suck and discharge fluid from the end direction, as shown in FIG. 7 to FIG. 9 , the two-stage single-acting vane pump, two stages as shown in FIGS. 12 to 13 Double acting slide pump.
  • the pump housing at the head end and the pump housing at the rear end can draw and discharge fluid from the lateral direction.
  • the relay of the multi-stage vane pump can be realized by the separation of the partition inside the diaphragm pump and the relay of the fluid transfer opening.
  • the slide pump suction port and the vane pump discharge port may not be disposed at the end of the vane pump, for example, the vane pump suction port and the vane pump discharge port may be disposed on the side of the vane pump Toward, either one of the vane pump suction port and the vane pump discharge port is provided at the end of the vane pump, and the other is disposed at the lateral direction of the vane pump.
  • the slide pump suction port and the vane pump discharge port are both disposed at the end of the vane pump to save space and facilitate processing.

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Abstract

一种滑片泵和利用滑片泵输送流体的方法，所述滑片泵具有筒状的泵壳（5），泵壳（5）中设有：驱动轴（1）、套在驱动轴上的转子（3）、设置在转子（3）上的滑片（4），滑片（4）与泵壳（5）的内腔接触密封，泵壳（5）的端部设有端盖，滑片泵还具有滑片泵吸入口（70）和滑片泵排出口（80），滑片泵吸入口（70）和/或滑片泵排出口（80）位于泵壳的端盖上。另一种滑片泵，所述滑片泵包括多个筒状的泵壳（25），滑片泵还具有滑片泵吸入口（270）和滑片泵排出口（280），滑片泵吸入口（270）和/或滑片泵排出口（280）分别位于端盖上，各隔板（22）上均设有贯穿各隔板上下端面的流体中转开口（24）。所述利用滑片泵输送流体的方法从泵壳的端部方向进行吸入和/或排出流体以进行泵送。

Description

滑片泵和利用滑片泵输送流体的方法
技术领域
本发明涉及液压领域， 具体而言， 涉及一种滑片泵和利用滑片泵输送流体的方法。 背景技术
滑片泵一种常用的容积式泵，广泛用于集输和举升的工业领域， 其具有很强的自吸能 力， 特别适用于油船码头卸油， 船上货油， 扫舱， 火车卸槽等场合， 及油罐车， 加油车和 油库、 加油站油料输送。 滑片泵可用于输送轻质油料， 而粘油效果更佳。 普通单作用滑片 泵工作原理如图 1所示。 一般单作用滑片泵主要由以下几部分组成： 驱动轴 1、 连接键 2、 转子 3、 滑片 4也称叶片、 定子也称泵壳 5。 驱动轴， 设置在所述泵壳中， 转子， 套在所 述驱动轴上并与所述驱动轴固定连接， 滑片， 从所述转子的侧向伸出并位于所述转子与所 述泵壳之间。 当电机或其它原动机旋转驱动轴 1时， 驱动轴 1通过键 2带动转子 3旋转， 转子 3带动滑片 4在泵壳 5的偏心腔室内转动， 叶片 4在离心力的作用下与定子内腔接触 密封， 由于叶片 4与定子 5构成腔室的容积变化， 使滑片泵可以对流体产生抽吸和挤压作 用。
与普通单作用滑片泵对应， 将定子或泵壳 5内腔的轮廓线修改为对称的椭圆形状或近 似椭圆形状， 轮廓线可以为多种曲线方程， 同时在定子或泵壳 5设置吸入口、 和排出口各 2个， 通常吸入口和排出口的周向间隔角度为 90° ， 这就是目前常用的双作用滑片泵， 见 图 2所示。 驱动轴旋转一圈， 双作用滑片泵吸入排出各两次。 与单作用滑片泵相比， 由于 结构和受力载荷对称， 双作用滑片泵往往可以获得更大排量， 同时降低滑片泵的噪声， 提 高驱动轴等部件的可靠性。
图 3给出了现有的一种普通单作用滑片泵的基本三维结构。 主要由以下几部分组成： 驱动轴 1、 端盖 6、 定子或泵壳 5、 转子 3及滑片 4。
上述工业中常见的滑片泵（包括单作用滑片泵和双作用滑片泵）在工作中都是单独使 用的， 即其输送介质从低压端吸入， 从高压端排出， 吸入口和排出口均设置在定子（或泵 壳） 的侧向， 这种方式为径向吸入和排出的旁通式结构， 例如， 日本专利 JP1-177478A, 以及中国专利 CN2379622Y，都采用径向吸入和排出的旁通式结构， 使得吸入和排出的方向 往往与滑片泵的旋转轴垂直， 吸入和排出的方向连接吸入和排出的管路后， 增加了滑片泵 的径向尺寸， 造成滑片泵体积较大， 很难适应狭小的管筒状空间， 而且这种径向吸入和排 出的旁通式结构需要很大的径向尺寸才能达到举升流体， （例如举升石油）的排量和压力， 无法安装在尺寸有限的套管内。 另外， 上述现有的滑片泵由于采用径向吸入和排出的旁通 式结构， 如果要下降到油井中进行举升原油， 则会在下降到油井的过程中， 径向设置的吸 入和排出的管路会受到破坏， 难以安全稳定的安装在井下， 而且径向设置的吸入和排出的 管路难以承受井下巨大压力和腐蚀， 不能在原油淹没工况下工作， 所以， 径向吸入和排 出的旁通式结构限制了滑片泵在井下举升方面的应用。
另外， 为了提高滑片泵的泵送压力， 往往需要提高原动机的转速， 因为散热等条件及 很多情况的限制， 带动滑片泵的原动机的速度难以提高。 普通滑片泵的这些特点限制了其 在一些工业领域的应用。
发明内容
本发明提供一种滑片泵和利用滑片泵输送流体的方法， 以解决现有的滑片泵径向尺寸 大、 滑片泵体积较大、 很难适应狭小的管筒状空间的问题。 此外， 本发明还可以解决滑片 泵的泵送压力较小的问题。
为此， 本发明提出一种滑片泵， 所述滑片泵具有筒状的泵壳， 所述泵壳中设有： 驱动 轴、 套在所述驱动轴上的转子、 设置在所述转子上的滑片， 所述滑片与所述泵壳的内腔接 触密封， 所述泵壳的端部设有端盖， 所述滑片泵还具有滑片泵吸入口和滑片泵排出口， 所 述滑片泵吸入口和 /或所述滑片泵排出口位于所述泵壳的端盖上。
进一步地， 所述滑片泵吸入口和滑片泵排出口均为一个， 在圆周方向上， 所述滑片泵 吸入口和滑片泵排出口关于所述驱动轴对称设置。
进一步地， 所述端盖包括： 底盖和位于所述底盖上方的顶盖， 所述滑片泵吸入口设置 在所述底盖上， 所述滑片泵排出口设置在所述顶盖上。
进一步地， 所述滑片泵吸入口包括： 设置在所述底盖上的第一吸入口和第二吸入口， 所述滑片泵排出口包括： 设置在所述顶盖上的第一排出口和第二排出口， 所述第一吸入口 和第二吸入口与所述驱动轴的轴心的连线为一条直线， 所述第一排出口和第二排出口与所 述驱动轴的轴心的连线为一条直线， 所述第一吸入口和第二吸入口的连线垂直所述第一排 出口和第二排出口的连线。
本发明还提出一种滑片泵，所述滑片泵具有从下至上输送流体的通道，所述滑片泵包 括多个筒状的泵壳， 多个所述泵壳按照从首端到尾端的方向依次衔接， 驱动轴， 穿过各所 述泵壳的内腔， 各所述泵壳套在所示驱动轴上， 多个所述泵壳至少包括首端的泵壳和尾端 的泵壳， 所述滑片泵的两端设有端盖， 一个端盖位于首端的泵壳的首端， 另一个端盖位于 尾端的泵壳的尾端；
所述滑片泵中设有套设在所述驱动轴上的 n个隔板， n大于等于 1， 所述隔板将相邻 两个所述泵壳分隔开， 每个泵壳中均设有套在所述驱动轴上的转子、 转子上设有滑片， 所 述滑片与所述泵壳的内腔接触密封；
所述滑片泵还具有滑片泵吸入口和滑片泵排出口， 所述滑片泵吸入口和 /或所述滑片 泵排出口分别位于所述端盖上， 所述各隔板上均设有贯穿所述各隔板上下端面的流体中转 开口， 所述输送流体的通道经过滑片泵吸入口、 流体中转开口和滑片泵排出口， 并且所述 输送流体的通道位于各所述泵壳的内腔中。
进一步地， 所述端盖包括： 底盖和位于所述底盖上方的顶盖， 所述滑片泵吸入口设置 在所述底盖上， 所述滑片泵排出口设置在所述顶盖上， 各所述隔板所在的平面垂直所述驱 动轴， 除了位于两端的泵壳外， 其余每个泵壳中， 下层隔板的流体中转开口为泵壳的吸入 口， 上层隔板的流体中转开口为泵壳的排出口； 所述滑片泵吸入口、 所述滑片泵排出口以 及各隔板上的流体中转开口的数目均为一个， 在圆周方向上， 所述滑片泵吸入口和相邻的 流体中转开口、 相邻的两个流体中转开口或滑片泵排出口与相邻的流体中转开口关于所述 驱动轴对称设置， 各泵壳的内腔均为形状相同的偏心腔室， 沿圆周方向， 上下相邻的两个 泵壳的设置方向呈 180度夹角。
进一步地， 所述端盖包括： 底盖和位于所述底盖上方的顶盖， 所述滑片泵吸入口设置 在所述底盖上， 所述滑片泵排出口设置在所述顶盖上， 各所述隔板所在的平面垂直所述驱 动轴， 每个泵壳中， 下层隔板的流体中转开口为该泵壳的吸入口， 上层隔板的流体中转开 口为该泵壳的排出口； 所述滑片泵吸入口、 所述滑片泵排出口以及各隔板上的流体中转开 口的数目均为两个， 两个所述滑片泵吸入口的周向间隔角度为 180度， 两个所述滑片泵排 出口的周向间隔角度为 180度，同一隔板上的两个流体中转开口的周向间隔角度为 180度； 所述滑片泵吸入口与相邻所述底盖的隔板的流体中转开口的周向间隔角度为 90度， 和 /或 上下相邻两隔板的流体中转开口的周向间隔角度为 90度， 和 /或所述滑片泵排出口与相邻 所述顶盖的隔板的流体中转开口的周向间隔角度为 90度， 各泵壳的内腔均为形状相同的 偏心腔室， 沿圆周方向， 上下相邻的两个泵壳的设置方向相互垂直。
进一步地， 所述滑片泵中设有一个套设在所述驱动轴上的隔板， 所述一个隔板所在的 平面垂直所述驱动轴， 所述一个隔板将所述滑片泵分为两个依次上下排布的泵壳， 分别为 上方的泵壳和下方的泵壳， 每个泵壳中均设有套在所述驱动轴上的转子， 所述转子通过连 接键与所述驱动轴固定连接，所述转子上设有滑片，所述滑片与所述泵壳的内腔接触密封; 所述端盖包括： 底盖和位于所述底盖上方的顶盖， 所述滑片泵吸入口设置在所述底盖上， 所述滑片泵排出口设置在所述顶盖上， 所述一个隔板上设有贯穿该隔板上下端面的流体中 转开口， 所述流体中转开口为下方的泵壳的排出口， 同时也是上方的泵壳的吸入口。
进一步地， 所述滑片泵吸入口、 所述滑片泵排出口以及一个所述隔板上的流体中转开 口的数目均为一个，在圆周方向上，所述滑片泵吸入口与一个所述隔板上的流体中转开口、 滑片泵排出口与一个所述隔板上的流体中转开口关于所述驱动轴对称设置， 上方的泵壳和 下方的泵壳的内腔均为形状相同的偏心腔室， 沿圆周方向， 上方的泵壳和下方的泵壳的设 置方向呈 180度夹角。
进一步地， 所述滑片泵吸入口、 所述滑片泵排出口、 以及所述一个隔板上的流体中转 开口的数目均为两个， 两个所述滑片泵吸入口的周向间隔角度为 180度， 两个所述滑片泵 排出口的周向间隔角度为 180度， 所述一个隔板上的两个流体中转开口的周向间隔角度为 180度； 所述滑片泵吸入口所述一个隔板的流体中转开口的周向间隔角度为 90度， 所述滑 片泵排出口与所述一个隔板的流体中转开口的周向间隔角度为 90 度， 上方的泵壳和下方 的泵壳的内腔均为形状相同的偏心腔室， 沿圆周方向， 上方的泵壳和下方的泵壳的设置方 向呈 90度夹角。
进一步地， 所述滑片泵包括两个依次衔接的筒状的泵壳， 所述滑片泵中设有套设在所 述驱动轴上的 1个隔板。
进一步地， 所述滑片泵包括三个依次衔接的筒状的泵壳， 所述滑片泵中设有依次套设 在所述驱动轴上的 2个隔板。
本发明还提出一种利用滑片泵输送流体的方法， 所述滑片泵具有筒状的泵壳， 所述泵 壳中设有驱动轴， 所述利用滑片泵输送流体的方法从所述泵壳的端部方向进行吸入和 /或 排出流体以进行泵送。
进一步地， 将所述滑片泵分隔成依次上下排布的多个泵壳， 多个所述泵壳按照从首端 到尾端的方向依次衔接， 每个泵壳均采用从所述泵壳的端部方向吸入和排出流体， 所述流 体从下至上输送， 流体被最下方泵壳吸入， 被最上方的泵壳泵送排出， 其中， 相邻的两个 泵壳通过隔板隔开， 所述隔板上设有贯穿所述隔板上下端面的流体中转开口， 所述流体通 过滑片泵吸入口、 流体中转开口和滑片泵排出口， ， 下方的泵壳排出的流体经过流体中转 开口被上方的泵壳吸入， 上方的泵壳从端部方向吸入的流体被再上方的泵壳吸入以形成吸 入和排出的接力， 直到吸入的流体被最上方的泵壳泵送排出。 进一步地， 所述吸入和 /或排出流体的方向与所述驱动轴的轴向平行。
进一步地， 将所述滑片泵分隔成多个泵壳， 多个所述泵壳按照从首端到尾端的方向依 次衔接， 多个所述泵壳至少包括位于最下方的首端的泵壳和位于最上方的尾端的泵壳， 所 述流体从下至上输送， 流体被最下方泵壳吸入， 被最上方的泵壳泵送排出， 首端的泵壳从 上端排出流体， 尾端的泵壳从下端吸入流体， 除首端的泵壳和尾端的泵壳之外， 其余每个 泵壳均采用从所述泵壳的端部方向吸入和排出流体， 包括首端的泵壳和尾端的泵壳在内的 各泵壳， 相邻的两个泵壳中， 下方的泵壳排出的流体被上方的泵壳吸入， 上方的泵壳吸入 的流体被再上方的泵壳吸入以形成吸入和排出的接力， 直到吸入的流体被最上方的泵壳泵 送排出。
进一步地， 所述吸入和 /或排出流体的方向与所述驱动轴的轴向平行。
本发明从所述泵壳的端部方向进行吸入和 /或排出流体， 通过转子的转动， 使得叶片 与泵壳所形成的腔体容积不断变化， 形成了滑片泵吸入口与泵壳内的低压腔连通， 滑片泵 排出口与高压腔连通， 产生了滑片泵吸入口和滑片泵排出口之间的压力差， 从而实现对流 体的泵送。
本发明从所述泵壳的端部方向进行吸入和 /或排出流体， 在实现对流体增压或泵送的 过程中， 由于滑片泵吸入口和滑片泵排出口存在上下高度差， 所以本发明还实现了流体势 能的变化， 而且当滑片泵吸入口和滑片泵排出口设置在泵壳的端部时， 最大限度的提高了 滑片泵对流体势能的变化影响， 尤其能够实现势能的提高， 这同传统的滑片泵吸入口和滑 片泵排出口设置在泵壳侧向， 滑片泵吸入口和滑片泵排出口之间的高度差不明显， 不能影 响流体势能的变化相比， 进步巨大， 使得滑片泵不仅具有增压或泵送的功能， 还使滑片泵 具有较高的举升能力， 使得滑片泵不局限于油船码头卸油， 船上货油， 扫舱， 火车卸槽等 场合， 及油罐车， 加油车和油库、 加油站油料输送， 还可以应用在需要举升的场合。
本发明避开了从泵壳的侧向进行吸入和排出流体， 减小了滑片泵的径向尺寸和径向体 积， 能够适应狭小的管筒状空间， 增加了滑片泵的应用范围。 由于本发明输送流体的通道 位于泵壳的内腔中， 因而无需设置现有技术的径向设置的吸入和排出的管路， 所以， 本发 明克服了现有的旁通式的滑片泵由于径向设置的吸入和排出的管路而造成的难以安全稳 定的安装在井下、 难以承受井下巨大压力和腐蚀和不能在原油淹没工况下工作等缺陷， 通 过泵壳或泵筒的保护，使得本滑片泵在实现举升和增压的同时，在结构上具有抗砂、抗气、 防腐、 耐压等综合性改善， 可以在原油淹没工况下工作， 实现 24小时无人职守下不间断 举升， 因而拓展了原油举升的方式， 比其他举升方式更耐高温。 另外， 本发明的输送流体的通道位于各所述筒状的定子的内腔中， 相对于现有的旁通 式的滑片泵径向设置的吸入和排出的管路进行输送液体， 本发明避免了通过离心作用将液 体输送至径向设置的吸入和排出的管路， 减少了液体输送效率的损失， 通过内部输送， 尤 其是轴向输送的方式， 增加了输送的流量和压力， 而且， 通过内部输送相对于旁通式的径 向吸入和排出， 本发明缩短了液体输送的路径， 更减少了液体传动损失， 减少了液体在径 向方向上压力和流速的折损。 此外， 本发明的吸入和排出流体的方向基本为直线或吸入和 排出流体的方向为轴向， 速度损失和效率损失小， 而现有技术的旁通式的吸入和排出， 流 体在吸入和排出的方向上发生较大的转变， 因而有技术的旁通式的吸入和排出产生较多的 速度损失、 效率损失。
本发明还通过设置依次上下排布的多个泵壳， 利用从端部方向泵送流体的吸入和排 出， 进而实现了多级滑片泵的接力增压， 使其更加适应管筒内流体的输送和举升作业， 可 以极大提升滑片泵的举升能力， 使得滑片泵可以应用于传统滑片泵应用的禁区， 例如流体 的举升， 包括石油开采， 扩大滑片泵的应用范围。 附图说明
本发明所采用的具体实施例， 将由以下的实施例及附呈附图作进一步的说明， 其中： 图 1为现有的单作用滑片泵工作原理示意图；
图 2为现有的双作用滑片泵工作原理示意图；
图 3用剖视方法示出了单作用滑片泵的三维结构；
图 4为根据本发明实施例的单级单作用轴流式滑片泵的分解结构示意图；
图 5用剖视方法示出了根据本发明实施例的单级单作用轴流式滑片泵的立体分解结 构；
图 6用剖视方法示出了根据本发明实施例的单级单作用轴流式滑片泵的立体组合结 构；
图 7为根据本发明实施例的两级单作用轴流式滑片泵的分解结构示意图；
图 8 用剖视方法示出了根据本发明实施例的两级单作用轴流式滑片泵的立体组合结 构；
图 9示出了根据本发明实施例的两级单作用轴流式滑片泵的立体组合结构； 图 10为根据本发明实施例的单级双作用轴流式滑片泵的分解结构示意图；
图 11 用剖视方法示出了根据本发明实施例的单级双作用轴流式滑片泵的立体分解结 构；
图 12用剖视方法示出了根据本发明实施例的两级双作用轴流式滑片泵的立体分解结 构；
图 13用剖视方法示出了根据本发明实施例的两级双作用轴流式滑片泵的立体组合结 构。
附图标号说明：
1、 驱动轴 2、 连接键、 3、 转子 4、 滑片 （或叶片） 5、 泵壳
6、 端盖 7、 吸入口 8、 排出口
61、 上端盖 63、 下端盖 70、 吸入口 80、 排出口
21、 驱动轴 22、 隔板 24、 流体中转口 23、 转子 261、 上端盖 263、 下端盖 25、 泵壳 270、 吸入口 280、 排出口 100、 一级泵 200、 二级泵
161、 上端盖（顶盖） 163、 下端盖（底盖） 170、 吸入口 180、 排出口
31、 驱动轴 32、 隔板 33、 转子 34、 流体中转口 361、 上端盖 363、 下端盖 235、 泵壳 370、 吸入口 380、 排出口 3100、 一级泵 3200、 二级泵 具体实施方式
为了对本发明的技术特征、 目的和效果有更加清楚的理解， 现对照附图说明本发明的 具体实施方式。
如图 4至图 6所示， 本发明提出一种滑片泵， 所述滑片泵具有筒状的泵壳 5， 所述泵 壳 5中设有： 驱动轴 1、 套在所述驱动轴上的转子 3， 转子 3通过连接键 2与驱动轴 1固 定连接、 设置在所述转子 3上的滑片 4， 所述滑片 4与所述泵壳 5的内腔接触密封， 所述 泵壳 5的端部设有端盖， 所述滑片泵还具有滑片泵吸入口 70和滑片泵排出口 80， 所述滑 片泵吸入口 70和 /或所述滑片泵排出口 80位于所述泵壳的端盖上， 为了结构紧凑， 所述 滑片泵吸入口 70和所述滑片泵排出口 80均位于所述泵壳的端盖上， 同时还最大限度的提 高了滑片泵对流体势能。 当然， 滑片泵吸入口 70或滑片泵排出口 80只要有一个从端部 方向输送流体， 另外一个可以仍然设置在泵壳的侧向， 也可以提高流体势能的功能， 也可 以减小部分区域内滑片泵的径向尺寸， 只不过滑片泵吸入口 70和滑片泵排出口 80同时设 置在泵壳的端盖上， 可以更好的实现滑片泵的径向尺寸最小化， 可以最大限度的提高流体 的势能。
除了所述滑片泵吸入口 70和所述滑片泵排出口 80均位于所述泵壳的端盖上之外， 关 于滑片泵中泵壳 5的形状、 驱动轴 1的形状、 滑片泵吸入口 70和所述滑片泵排出口 80滑 片泵的轴端密封及轴承支撑、 泵壳 5的端盖的形状以及滑片泵中的上述部件的连接关系、 以及低压吸入、 高压排出的工作原理不是本发明讨论的重点， 上述结构和工作原理可以参 考和采用现有的各种滑片泵的合适结构。例如，滑片泵吸入口与泵壳的低压腔连接或连通， 所述滑片泵排出口与泵壳的高压腔连接或连通。
图 4至图 6所示的为本发明的单级单作用轴流式滑片泵， 所述端盖包括： 底盖 63和 位于所述底盖上方的顶盖 61， 各所述端盖为圆盘状， 其中设有驱动轴 1穿过的轴孔， 各所 述端盖所在的平面垂直所述驱动轴 1， 这样便于驱动轴 1的旋转。 进一步地， 所述滑片泵 吸入口 70设置在所述底盖 63上， 所述滑片泵排出口 80设置在所述顶盖 61上。 滑片泵吸 入口 70和所述滑片泵排出口 80分别为贯穿底盖 63和顶盖 61的通孔， 所述滑片泵吸入口 和滑片泵排出口均为一个， 在圆周方向上， 所述滑片泵吸入口和滑片泵排出口关于所述驱 动轴对称设置， 滑片泵吸入口 70和所述滑片泵排出口 80的形状可以为长弧形， 当然也可 以为其他形状。
本发明的滑片泵， 从底端的滑片泵吸入口 70吸进低压流体， 流体在转子 3的转动中， 通过滑片泵转子的转动形成的容积的变化， 导致吸进的流体和排出的流体之间形成压力 差， 从顶盖 61的滑片泵排出口 80排出高压流体， 这样， 本发明从根本上避开了从泵壳的 侧向进行吸入和排出流体， 减小了滑片泵的径向尺寸和径向体积， 能够适应狭小的管筒状 空间， 增加了滑片泵的应用范围。 本发明不局限于只从端盖吸入和排出流体， 只要能够从 所述泵壳的端部方向进行吸入和排出流体的方法以进行泵送， 不管滑片泵是否设置端盖， 不管流体是否经过端盖， 本发明都能实现端向吸入和排出流体， 通常情况下， 流体的吸入 和排出方向与驱动轴 1的轴向一致或接近， 因而， 本发明的滑片泵也 （又）可以称为轴流 式滑片泵， 只要端向吸入和排出流体， 无论吸入和排出流体的方向与驱动轴的夹角， 例如 可以与驱动轴 1的轴向相交 15度、 30度、 60度等， 均与现有的在泵壳的侧向吸入和排出 流体的旁通式结构区别明显， 只不过流体的吸入和排出方向与驱动轴 1的轴向一致或接近 时， 本发明的滑片泵结构更紧凑。
进一步地， 如果在单作用轴流式滑片泵的端盖上使滑片泵吸入口 70和所述滑片泵排 出口 80的数目均变为两个， 则可以得到双作用滑片泵。 如图 10和图 11所示， 所述滑片 泵吸入口 170包括： 设置在所述底盖 163上的第一吸入口和第二吸入口， 所述滑片泵排出 口 180包括： 设置在所述顶盖 161上的第一排出口和第二排出口， 滑片泵吸入口与泵壳的 低压腔连接或连通， 所述滑片泵排出口与泵壳的高压腔连接或连通； 所述第一吸入口和第 二吸入口与所述驱动轴 1的轴心的连线为一条直线， 所述第一排出口和第二排出口与所述 驱动轴的轴心的连线为一条直线， 所述第一吸入口和第二吸入口的连线垂直所述第一排出 口和第二排出口的连线。 也就是各所述滑片泵吸入口与各所述滑片泵排出口的周向间隔角 度为 90度， 这样可以获得更大排量， 同时降低滑片泵的噪声， 提高驱动轴等部件的可靠 性。 至于其他方面， 例如， 关于转子 3通过连接键 2与驱动轴 1的连接， 以及泵壳 5内的 结构可以采用与单作用泵一样的结构。
如图 7至图 9所示，本发明还提出一种滑片泵，该滑片泵为两级单作用轴流式滑片泵。 所述滑片泵具有两个分体的筒状泵壳 25， 各泵壳 25按照从首端到尾端的方向依次衔接并 套在， 每个所述泵壳中设有驱动轴 21， 驱动轴 21可以为一个整体的轴， 该整体的轴穿过 各泵壳 25， 各所述泵壳套在所示驱动轴上， 滑片泵中设有一个套设在所述驱动轴 21上的 隔板 22， 所述隔板 22所在的平面垂直所述驱动轴 21， 所述隔板 22将所述滑片泵分为两 个依次上下排布的泵壳；
每个泵壳中均设有套在所述驱动轴上的转子 23， 所述转子 23通过连接键与所述驱动 轴 21 固定连接， 所述转子上设有滑片， 所述滑片与所述泵壳的内腔接触密封； 所述泵壳 的端部设有端盖， 所述端盖包括： 底盖 263和位于所述底盖上方的顶盖 261， 所述滑片泵 吸入口 270设置在所述底盖 263上， 所述滑片泵排出口 280设置在所述顶盖 261上， 所述 隔板 22上设有贯穿该隔板 22上下端面的流体中转开口 24。 隔板 22可以与各端盖的结构 相同， 例如均为圆盘状。流体中转开口 24、滑片泵吸入口 270和所述滑片泵排出口 280的 形状可以相同， 可以为长弧形。 这样， 隔板 22可以与各端盖可以相互替换， 便于制作安 装。 其中， 各泵壳可以焊接在隔板 22上。
下方的泵壳及其中的部件形成一级泵 100， 上方的泵壳及其中的部件形成二级泵 200， 流体中转开口 24 既是上一级泵的排出口， 又是下一级泵的吸入口； 两级轴流滑片泵的定 子 （或称为泵壳） 180 ° 对置， 从而也实现了上一级泵和下一级泵高压腔和低压腔室方向 的 180° 对置， 也就是， 流体中转开口 24与一级泵 100的高压腔连接， 同时与二级泵 200 的低压腔连接， 实现两级轴流滑片泵之间的隔板 22 能同时作为排出口 （上一级泵的排出 口）和吸入口 （下一级泵的吸入口） 。 对于两级 (或多级） 单作用轴流滑片泵，当驱动轴旋 转时，驱动轴同时带动各级的转子和滑片运动，一级轴流滑片泵 100通过从滑片泵吸入口 270吸入流体和从流体中转开口 24排出流体，将流体增压排入二级轴流滑片泵 200的吸入 端，二级轴流滑片泵 200的吸入端也是流体中转开口 24， 即也是一级轴流滑片泵 100的排 出端， 二级轴流滑片泵对流体进行增压后从滑片泵排出口 280排出。 如果单级滑片泵的增 压倍数为 m， 则经过两级轴流滑片泵增压后， 滑片泵的整体增压倍数为 m的平方， 经过三 级， 则整体增压倍数为 m的立方， 经过 n级， 则滑片泵整体增压倍数为 m的 n次方， 通过 以上设计可以实现多级单作用轴流滑片泵的接力增压， 而且效果显著。
对于二级或多级滑片泵， 经过隔板 22的分隔， 使得各泵壳相互独立， 使得每个泵壳 都能形成对流体的泵送， 又经过流体中转开口 24 的中转， 使得各泵壳的吸入和排出相互 关联， 形成了多级滑片泵的接力增压。 当然， 只要在滑片泵的内部经过隔板 22 的分隔以 及流体中转开口 24 的中转就能实现多级滑片泵的接力增压， 至于滑片泵吸入口和所述滑 片泵排出口可以不设置在滑片泵端部， 例如， 滑片泵吸入口和所述滑片泵排出口可以都设 置在滑片泵的侧向， 或者滑片泵吸入口和所述滑片泵排出口中的一个设置在滑片泵的端 部， 另一个设置在滑片泵的侧向， 只不过滑片泵吸入口和所述滑片泵排出口都设置在滑片 泵端部更有利于节约空间， 也便于加工。
当然， 根据图 7至图 9所示， 本发明的滑片泵不局限于两级泵， 还可以为更多级泵。 例如， 所述滑片泵包括 3个或更多筒状的泵壳， 多个所述泵壳按照从首端到尾端的方向依 次衔接， 驱动轴， 穿过各所述泵壳的内腔， 多个所述泵壳至少包括首端的泵壳和尾端的泵 壳， 所述滑片泵的两端设有端盖， 一个端盖位于首端的泵壳的首端， 另一个端盖位于尾端 的泵壳的尾端； 所述滑片泵中设有套设在所述驱动轴上的 2个或更多隔板， 所述隔板将 相邻两个所述泵壳分隔开，每个泵壳中均设有套在所述驱动轴上的转子、转子上设有滑片， 所述滑片与所述泵壳的内腔接触密封； 所述滑片泵还具有滑片泵吸入口和滑片泵排出口， 所述滑片泵吸入口和 /或所述滑片泵排出口分别位于所述端盖上， 所述各隔板上均设有贯 穿所述各隔板上下端面的流体中转开口。
对于上述具有三级或更多级泵的滑片泵来说，每个泵壳的结构和功能均可与两级泵的 结构和功能相同或类似， 都是采用隔板的分隔， 使得各泵壳相互独立， 使得每个泵壳都能 形成对流体的泵送， 又经过流体中转开口的中转， 使得各泵壳的吸入和排出相互关联， 形 成了多级滑片泵的接力增压。 例如， 对于具有三级或更多级泵的滑片泵来说， 首端的泵壳 和尾端的泵壳与两级滑片泵中的上方的泵壳和下方的泵壳结构相同， 具有三级或更多级泵 的滑片泵还具有位于首尾两端之间的中间的泵壳， 中间的泵壳则是由上下相邻的隔板围成 的一级泵， 隔板上的流体中转开口仍然起到流体中转的作用， 即所述流体中转开口为下方 的泵壳的排出口， 同时也是上方的泵壳的吸入口， 该中间的泵壳中， 流体从下层的流体中 转开口吸入， 从上层的流体中转开口排出， 滑片泵的最初吸入流体依然从滑片泵吸入口吸 入， 最终排出流体仍然从滑片泵排出口排出， 流体中转开口与低一级泵的高压腔连接， 同 时与高一级泵的低压腔连接， 形成流体从低级泵向高级泵的增压。
如图 12至图 13所示， 滑片泵为两级双作用滑片泵。 两级双作用滑片泵与两级单作用 滑片泵的主要区别在于， 两级双作用滑片泵比两级单作用滑片泵多个一个所述滑片泵吸入 口和一个所述滑片泵排出口。 所述滑片泵吸入口 370设置在上端盖（也称顶盖） 361上， 所述滑片泵排出口 380设置在下端盖（也称底盖） 363上。 所述滑片泵吸入口 370、 所述 滑片泵排出口 380、 以及所述隔板 32上的流体中转开口 34的数目均为两个， 两个所述滑 片泵吸入口 370的周向间隔角度为 180度， 两个所述滑片泵排出口 380的周向间隔角度为 180度， 所述一个隔板上的两个流体中转开口 34的周向间隔角度为 180度； 所述滑片泵吸 入口 370与所述隔板 32的流体中转开口 34的周向间隔角度为 90度， 所述滑片泵排出口 380与所述隔板 32的流体中转开口 34的周向间隔角度为 90度。 各泵壳 35的内腔均可以 为形状相同的偏心腔室，沿圆周方向，上下相邻的两个泵壳的设置方向相互垂直，也就是， 流体中转开口 34与一级泵 3100的高压腔连接， 同时与二级泵 3200的低压腔连接。 其他 与双级单作用滑片泵的结构相同或类似，例如，所述滑片泵吸入口 370设置在所述底盖 363 上，所述滑片泵排出口 380设置在所述顶盖 361上，驱动轴 31垂直穿过隔板 32、底盖 363 和顶盖 361， 驱动轴 31上设有转子 33和叶片， 实现两级轴流滑片泵之间的隔板能同时作 为排出口 （上一级泵的排出口）和吸入口 （下一级泵的吸入口） 。 流体可以从两个滑片泵 吸入口 370吸入到一级泵 3100中，经过增压后从两个流体中转开口 34被排出到二级泵 3200 中， 二级泵 3200从两个流体中转开口 34吸入一级泵 3100排出的流体经过增压后从滑片 泵排出口 380排出。 经过两个泵壳的两级增压后， 从两个滑片泵排出口 380排出， 既实现 了多级增压， 又实现了更大的流体排量， 同时降低滑片泵的噪声， 提高驱动轴等部件的可 靠性。 当然， 各泵壳 35的内腔及转子的结构不限于偏心腔室结构， 还包括其他种类。
对于两级 (或更多级） 双作用轴流滑片泵，当驱动轴旋转时，驱动轴同时带动各级的转 子和滑片运动，一级双作用轴流滑片泵通过吸入和排出将流体增压排入二级双作用轴流滑 片泵的吸入端，二级双作用轴流滑片泵对流体进行增压后排出。 通过以上设计可以实现多 级双作用轴流滑片泵的接力增压。
例如， 三级以上的双作用轴流滑片泵， 所述泵壳中设有一个套设在所述驱动轴上的隔 板， 所述一个隔板所在的平面垂直所述驱动轴， 所述一个隔板将所述泵壳的内腔分为两个 依次上下排布的泵壳， 每个泵壳中均设有套在所述驱动轴上的转子， 所述转子通过连接键 与所述驱动轴固定连接， 所述转子上设有滑片， 所述滑片与所述泵壳的内腔接触密封； 所 述端盖包括： 底盖和位于所述底盖上方的顶盖， 所述滑片泵吸入口设置在所述底盖上， 所 述滑片泵排出口设置在所述顶盖上， 所述一个隔板上设有贯穿该隔板上下端面的流体中转 开口； 所述滑片泵吸入口、 所述滑片泵排出口、 以及所述一个隔板上的流体中转开口的数 目均为两个， 两个所述滑片泵吸入口的周向间隔角度为 180度， 两个所述滑片泵排出口的 周向间隔角度为 180度， 所述一个隔板上的两个流体中转开口的周向间隔角度为 180度； 所述滑片泵吸入口与所述一个隔板的流体中转开口的周向间隔角度为 90 度， 所述滑片泵 排出口与所述一个隔板的流体中转开口的周向间隔角度为 90 度。 这种三级或多级双作用 滑片泵能够大幅增加滑片泵排量， 尤其适用于井下狭窄的空间内。
本发明还提出一种利用滑片泵输送流体的方法， 所述滑片泵具有筒状的泵壳， 所述泵 壳中设有驱动轴， 所述利用滑片泵输送流体的方法从所述泵壳的端部方向进行吸入和排出 流体以进行泵送。 如图 4至图 6所示的单级单作用滑片泵、 如图 7至图 9所示的两级单作 用滑片泵、 如图 10至图 11所示的单级双作用滑片泵、 如图 12至图 13所示的两级双作用 滑片泵均采用从所述泵壳的端部方向进行吸入和排出流体以进行泵送， 例如， 可以从上端 到下端输送， 还可以从下端到上端输送， 上述各实施例示出的是采用在端盖上设置吸入口 和排出口， 本发明并不局限于在端盖上设置吸入口和排出口以从所述泵壳的端部方向进行 吸入和排出流体， 还可以采用其他从所述泵壳的端部方向进行吸入和排出流体， 例如对不 设置端盖的泵壳从所述泵壳的端部方向进行吸入和排出流体。 在此基础上， 更多级单作用 以及更多级双作用均可以采用增加泵壳、 隔板以及流体中转开口的方式增加泵送的级数， 实现更多级的泵送。
本发明的这种从所述泵壳的端部方向进行吸入和排出流体以进行泵送的方法， 使相邻 两级泵壳之间在滑片泵内部实现了上方的泵壳吸入下方泵壳的排出， 实现了两级泵壳之间 吸入和排出的零距离转换。 本发明不局限于只从端盖吸入和排出流体， 本发明的端盖也不 局限于圆盘状， 只要能够从所述泵壳的端部方向进行吸入和排出流体的方法以进行泵送， 不管滑片泵是否设置端盖，不管流体是否经过端盖，本发明都能实现端向吸入和排出流体。
对于单级滑片泵， 滑片泵吸入口和所述滑片泵排出口中的一个设置在滑片泵的端部， 另一个可以设置在滑片泵的侧向， 也能实现本发明节省空间的目的， 只不过滑片泵吸入口 和所述滑片泵排出口都设置在滑片泵端部更有利于节约空间， 也便于加工。
对于多级滑片泵， 只要在滑片泵的内部经过隔板的分隔以及流体中转开口的中转就能 实现多级滑片泵的接力增压， 至于滑片泵吸入口和所述滑片泵排出口可以不设置在滑片泵 端部， 例如， 滑片泵吸入口和所述滑片泵排出口可以都设置在滑片泵的侧向， 或者滑片泵 吸入口和所述滑片泵排出口中的一个设置在滑片泵的端部， 另一个设置在滑片泵的侧向。 只不过滑片泵吸入口和所述滑片泵排出口都设置在滑片泵端部更有利于节约空间， 也便于 加工。 当然， 流体的吸入和排出方向与驱动轴的轴向一致或接近时， 本发明的滑片泵结构 更紧凑， 输送效果更好， 径向尺寸更为理想。
进一步地， 将所述滑片泵分隔成依次上下排布的多个泵壳， 多个所述泵壳按照从首端 到尾端的方向依次衔接， 每个泵壳均采用从所述泵壳的端部方向吸入和排出流体， 所述流 体从下至上输送， 流体被最下方泵壳吸入， 被最上方的泵壳泵送排出， 其中， 相邻的两个 泵壳中， 下方的泵壳排出的流体被上方的泵壳吸入， 上方的泵壳吸入的流体被再上方的泵 壳吸入以形成吸入和排出的接力， 直到吸入的流体被最上方的泵壳泵送排出。 如图 7至图 9所示的两级单作用滑片泵、 如图 12至图 13所示的两级双作用滑片泵， 滑片泵的内部经 过隔板的分隔以及流体中转开口的中转就能实现多级滑片泵的接力增压， 这种设置多个泵 壳的方式可以实现多级滑片泵的接力增压， 这种增压方式大大改善了滑片泵的增压效果和 举升作用。
进一步地， 将所述滑片泵分隔成多个泵壳， 多个所述泵壳按照从首端到尾端的方向依 次衔接， 多个所述泵壳至少包括位于最下方的首端的泵壳和位于最上方的尾端的泵壳， 所 述流体从下至上输送， 流体被最下方泵壳吸入， 被最上方的泵壳泵送排出， 首端的泵壳从 上端排出流体， 尾端的泵壳从下端吸入流体， 除首端的泵壳和尾端的泵壳之外， 其余每个 泵壳均采用从所述泵壳的端部方向吸入和排出流体， 包括首端的泵壳和尾端的泵壳在内的 各泵壳， 相邻的两个泵壳中， 下方的泵壳排出的流体被上方的泵壳吸入， 上方的泵壳吸入 的流体被再上方的泵壳吸入以形成吸入和排出的接力， 直到吸入的流体被最上方的泵壳泵 送排出。 其中， 首端的泵壳和尾端的泵壳可以从端部方向吸入和排出流体， 如图 7至图 9 所示的两级单作用滑片泵、 如图 12至图 13所示的的两级双作用滑片泵。
此外， 首端的泵壳和尾端的泵壳可以从侧向方向吸入和排出流体， 只要在滑片泵的内 部经过隔板的分隔以及流体中转开口的中转就能实现多级滑片泵的接力增压， 至于滑片泵 吸入口和所述滑片泵排出口可以不设置在滑片泵端部， 例如， 滑片泵吸入口和所述滑片泵 排出口可以都设置在滑片泵的侧向， 或者滑片泵吸入口和所述滑片泵排出口中的一个设置 在滑片泵的端部， 另一个设置在滑片泵的侧向。 只不过滑片泵吸入口和所述滑片泵排出口 都设置在滑片泵端部更有利于节约空间， 也便于加工。
以上所述仅为本发明示意性的具体实施方式， 并非用以限定本发明的范围。 为本发明 的各组成部分在不冲突的条件下可以相互组合， 任何本领域的技术人员， 在不脱离本发明 的构思和原则的前提下所作出的等同变化与修改， 均应属于本发明保护的范围。

Claims

权利要求书
1、 一种滑片泵， 所述滑片泵具有从下至上输送流体的通道， 其特征在于， 所述滑片 泵包括多个筒状的泵壳， 多个所述泵壳按照从首端到尾端的方向依次衔接， 驱动轴， 穿过 各所述泵壳的内腔， 各所述泵壳套在所述驱动轴上， 多个所述泵壳至少包括首端的泵壳和 尾端的泵壳， 所述滑片泵的两端设有端盖， 一个端盖位于首端的泵壳的首端， 另一个端盖 位于尾端的泵壳的尾端；
所述滑片泵中设有套设在所述驱动轴上的 n个隔板， n大于等于 1， 所述隔板将相 邻两个所述泵壳分隔开， 每个泵壳中均设有套在所述驱动轴上的转子， 转子上设有滑片， 所述滑片与所述泵壳的内腔接触密封；
所述滑片泵还具有滑片泵吸入口和滑片泵排出口， 所述滑片泵吸入口和 /或所述滑片 泵排出口分别位于所述端盖上，所述各隔板上均设有贯穿所述各隔板上下端面的流体中转 开口， 所述输送流体的通道经过滑片泵吸入口、流体中转开口和滑片泵排出口， 并且所述 输送流体的通道位于各所述泵壳的内腔中。
2、 如权利要求 1所述的滑片泵， 其特征在于， 所述端盖包括： 底盖和位于所述底盖 上方的顶盖，所述滑片泵吸入口设置在所述底盖上，所述滑片泵排出口设置在所述顶盖上， 各所述隔板所在的平面垂直所述驱动轴， 除了位于两端的泵壳外， 其余每个泵壳中， 下层 隔板的流体中转开口为该泵壳的吸入口， 上层隔板的流体中转开口为该泵壳的排出口； 所 述滑片泵吸入口、所述滑片泵排出口以及各隔板上的流体中转开口的数目均为一个， 在圆 周方向上， 所述滑片泵吸入口和相邻的流体中转开口、相邻的两个流体中转开口或滑片泵 排出口与相邻的流体中转开口关于所述驱动轴对称设置，各泵壳的内腔均为形状相同的偏 心腔室， 沿圆周方向， 上下相邻的两个泵壳的设置方向呈 180度夹角。
3、 如权利要求 1所述的滑片泵， 其特征在于， 所述端盖包括： 底盖和位于所述底盖 上方的顶盖，所述滑片泵吸入口设置在所述底盖上，所述滑片泵排出口设置在所述顶盖上， 各所述隔板所在的平面垂直所述驱动轴， 除了位于两端的泵壳外， 其余每个泵壳中， 下层 隔板的流体中转开口为该泵壳的吸入口， 上层隔板的流体中转开口为该泵壳的排出口； 所 述滑片泵吸入口、所述滑片泵排出口以及各隔板上的流体中转开口的数目均为两个， 两个 所述滑片泵吸入口的周向间隔角度为 180度， 两个所述滑片泵排出口的周向间隔角度为 180度， 同一隔板上的两个流体中转开口的周向间隔角度为 180度； 所述滑片泵吸入口与 相邻所述底盖的隔板的流体中转开口的周向间隔角度为 90度，和 /或上下相邻两隔板的流 体中转开口的周向间隔角度为 90度，和 /或所述滑片泵排出口与相邻所述顶盖的隔板的流 体中转开口的周向间隔角度为 90度， 各泵壳的内腔均为形状相同的偏心腔室， 沿圆周方 向， 上下相邻的两个泵壳的设置方向相互垂直。
4、 如权利要求 1所述的滑片泵， 其特征在于， 所述滑片泵中设有一个套设在所述驱 动轴上的隔板， 所述一个隔板所在的平面垂直所述驱动轴， 所述一个隔板将所述滑片泵分 为两个依次上下排布的泵壳分别为上方的泵壳和下方的泵壳，每个泵壳中均设有套在所述 驱动轴上的转子， 所述转子通过连接键与所述驱动轴固定连接， 所述转子上设有滑片， 所 述滑片与所述泵壳的内腔接触密封； 所述端盖包括： 底盖和位于所述底盖上方的顶盖， 所 述滑片泵吸入口设置在所述底盖上， 所述滑片泵排出口设置在所述顶盖上， 所述一个隔板 上设有贯穿该隔板上下端面的流体中转开口； 所述流体中转开口为下方的泵壳的排出口， 同时也是上方的泵壳的吸入口。
5、 如权利要求 4所述的滑片泵， 其特征在于， 所述滑片泵吸入口、 所述滑片泵排出 口以及一个所述隔板上的流体中转开口的数目均为一个， 在圆周方向上， 所述滑片泵吸入 口与一个所述隔板上的流体中转开口、滑片泵排出口与一个所述隔板上的流体中转开口关 于所述驱动轴对称设置， 上方的泵壳和下方的泵壳的内腔均为形状相同的偏心腔室， 沿圆 周方向， 上方的泵壳和下方的泵壳的设置方向呈 180度夹角。
6、 如权利要求 4所述的滑片泵， 其特征在于， 所述滑片泵吸入口、 所述滑片泵排出 口、 以及所述一个隔板上的流体中转开口的数目均为两个， 两个所述滑片泵吸入口的周向 间隔角度为 180度， 两个所述滑片泵排出口的周向间隔角度为 180度， 所述一个隔板上的 两个流体中转开口的周向间隔角度为 180度；所述滑片泵吸入口与所述一个隔板的流体中 转开口的周向间隔角度为 90度， 所述滑片泵排出口与所述一个隔板的流体中转开口的周 向间隔角度为 90度， 上方的泵壳和下方的泵壳的内腔均为形状相同的偏心腔室， 沿圆周 方向， 上方的泵壳和下方的泵壳的设置方向呈 90度夹角。
7、 如权利要求 2或 3所述的滑片泵， 其特征在于， 所述滑片泵包括两个依次衔接的 筒状的泵壳， 所述滑片泵中设有套设在所述驱动轴上的 1个隔板。
8、 如权利要求 2或 3所述的滑片泵， 其特征在于， 所述滑片泵包括三个依次衔接的 筒状的泵壳， 所述滑片泵中设有依次套设在所述驱动轴上的 2个隔板。
9、 一种利用滑片泵输送流体的方法， 所述滑片泵具有筒状的泵壳， 所述泵壳中设有 驱动轴， 所述利用滑片泵输送流体的方法从所述泵壳的端部方向进行吸入和 /或排出流体 以进行泵送， 其特征在于， 将所述滑片泵分隔成多个泵壳， 多个所述泵壳按照从首端到尾 端的方向依次衔接， 每个泵壳均采用从所述泵壳的端部方向吸入和排出流体， 所述流体从 下至上输送， 流体被最下方泵壳吸入， 被最上方的泵壳泵送排出， 其中， 相邻的两个泵壳 通过隔板隔开， 所述隔板上设有贯穿所述隔板上下端面的流体中转开口， 所述流体通过滑 片泵吸入口、流体中转开口和滑片泵排出口， 下方的泵壳排出的流体经过流体中转开口被 上方的泵壳吸入，上方的泵壳吸入的流体被再上方的泵壳从端部方向吸入以形成吸入和排 出的接力， 直到吸入的流体被最上方的泵壳泵送排出。
10、 如权利要求 9所述的利用滑片泵输送流体的方法， 其特征在于， 将所述滑片泵 分隔成多个泵壳， 多个所述泵壳按照从首端到尾端的方向依次衔接， 多个所述泵壳至少包 括位于最下方的首端的泵壳和位于最上方的尾端的泵壳， 所述流体从下至上输送， 流体被 最下方泵壳吸入， 被最上方的泵壳泵送排出， 首端的泵壳从上端排出流体， 尾端的泵壳从 下端吸入流体， 除首端的泵壳和尾端的泵壳之外， 其余每个泵壳均采用从所述泵壳的端部 方向吸入和排出流体， 包括首端的泵壳和尾端的泵壳在内的各泵壳， 相邻的两个泵壳中， 下方的泵壳排出的流体被上方的泵壳吸入，上方的泵壳吸入的流体被再上方的泵壳吸入以 形成吸入和排出的接力， 直到吸入的流体被最上方的泵壳泵送排出。
11、 如权利要求 9至 10中任一项所述的利用滑片泵输送流体的方法， 其特征在于， 所述吸入和 /或排出流体的方向与所述驱动轴的轴向平行。
PCT/CN2012/083306 2012-03-02 2012-10-22 滑片泵和利用滑片泵输送流体的方法 Ceased WO2013127182A1 (zh)

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US11717670B2 (en) 2017-06-07 2023-08-08 Shifamed Holdings, LLP Intravascular fluid movement devices, systems, and methods of use
US11511103B2 (en) 2017-11-13 2022-11-29 Shifamed Holdings, Llc Intravascular fluid movement devices, systems, and methods of use
US12076545B2 (en) 2018-02-01 2024-09-03 Shifamed Holdings, Llc Intravascular blood pumps and methods of use and manufacture
US11229784B2 (en) 2018-02-01 2022-01-25 Shifamed Holdings, Llc Intravascular blood pumps and methods of use and manufacture
US10722631B2 (en) 2018-02-01 2020-07-28 Shifamed Holdings, Llc Intravascular blood pumps and methods of use and manufacture
US12161857B2 (en) 2018-07-31 2024-12-10 Shifamed Holdings, Llc Intravascular blood pumps and methods of use
US12220570B2 (en) 2018-10-05 2025-02-11 Shifamed Holdings, Llc Intravascular blood pumps and methods of use
US11964145B2 (en) 2019-07-12 2024-04-23 Shifamed Holdings, Llc Intravascular blood pumps and methods of manufacture and use
US11654275B2 (en) 2019-07-22 2023-05-23 Shifamed Holdings, Llc Intravascular blood pumps with struts and methods of use and manufacture
US12465748B2 (en) 2019-08-07 2025-11-11 Supira Medical, Inc. Catheter blood pumps and collapsible pump housings
US12102815B2 (en) 2019-09-25 2024-10-01 Shifamed Holdings, Llc Catheter blood pumps and collapsible pump housings
US12121713B2 (en) 2019-09-25 2024-10-22 Shifamed Holdings, Llc Catheter blood pumps and collapsible blood conduits
US11724089B2 (en) 2019-09-25 2023-08-15 Shifamed Holdings, Llc Intravascular blood pump systems and methods of use and control thereof
US12409310B2 (en) 2019-12-11 2025-09-09 Shifamed Holdings, Llc Descending aorta and vena cava blood pumps
US12599758B2 (en) 2019-12-19 2026-04-14 Shifamed Holdings, Llc Intravascular blood pumps, motors, and fluid control

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