阅读说明：本技术 一种双端贯穿轴的螺旋反曲轮油泵 (Spiral reverse-curve wheel oil pump with two ends penetrating through shaft ) 是由 刘小龙 于 2020-04-07 设计创作，主要内容包括：本发明公开了一种双端贯穿轴的螺旋反曲轮油泵,包括主轴、螺旋轮、泵壳、泵盖、柱塞组件,泵壳内部中空并在一端安装泵盖,主轴穿过泵壳、泵盖,螺旋轮安装在主轴上,螺旋轮位于泵壳内；柱塞组件包括至少两个柱塞,螺旋轮包括端板和设置在端板一侧的螺旋形叶片,端板外缘紧贴泵壳内缘面,螺旋形叶片背离端板的一侧敞开,螺旋形叶片构造螺旋形的流道,流道宽度保持不变,柱塞可沿轴向插入流道内,柱塞分布在螺旋轮径向的两个圆周角度,柱塞插入流道内后随着螺旋轮的旋转而将柱塞一侧介质往螺旋轮中央或外缘挤送。(The invention discloses a spiral reverse-curve wheel oil pump with two ends penetrating through a shaft, which comprises a main shaft, a spiral wheel, a pump shell, a pump cover and a plunger assembly, wherein the pump shell is hollow, the pump cover is arranged at one end of the pump shell, the main shaft penetrates through the pump shell and the pump cover, the spiral wheel is arranged on the main shaft, and the spiral wheel is positioned in the pump shell; the plunger assembly comprises at least two plungers, the spiral wheel comprises an end plate and spiral blades arranged on one side of the end plate, the outer edge of the end plate is tightly attached to the inner edge face of the pump shell, one side, deviating from the end plate, of each spiral blade is opened, each spiral blade is provided with a spiral flow channel, the width of each flow channel is kept unchanged, the plungers can be inserted into the flow channels along the axial direction, the plungers are distributed at two radial circumferential angles of the spiral wheel, and media on one side of the plungers are extruded to the center or the outer edge of the spiral wheel along with the rotation of the spiral wheel after the.)

1. The utility model provides a spiral recurved wheel oil pump of axle is run through to bi-polar which characterized in that: the spiral reverse-bending oil pump comprises a main shaft (1), a spiral wheel (2), a pump shell (3), a pump cover (4) and a plunger assembly (5), wherein the pump shell (3) is hollow, the pump cover (4) is installed at one end of the pump shell, the main shaft (1) penetrates through the pump shell (3) and the pump cover (4), the spiral wheel (2) is installed on the main shaft (1), and the spiral wheel (2) is located in the pump shell (3);

the plunger assembly (5) comprises at least two plungers (51), the spiral wheel (2) comprises an end plate (20) and a spiral blade arranged on one side of the end plate, the outer edge of the end plate (20) is tightly attached to the inner edge surface of the pump shell (3), one side of the spiral blade, which is far away from the end plate (20), is opened, the spiral blade is used for constructing a spiral flow channel (21), the width of the flow channel (21) is kept unchanged, the plungers (51) can be axially inserted into the flow channel (21), the plungers (51) are distributed at two radial circumferential angles of the spiral wheel (2), and a medium on one side of the plunger (51) is extruded to the center or the outer edge of the spiral wheel (2) along with the rotation of the spiral wheel (2) after the plungers (51) are inserted into the flow channel (21).

2. The helical reverse-curve wheel oil pump with double ends penetrating through a shaft as claimed in claim 1, wherein: an impeller core opening (22) communicated with the back surface of the spiral wheel (2) is arranged at the end part of the flow channel (21) of the spiral wheel (2) close to the center;

the outer edge of the end face of the pump cover (4) is provided with an interface (41), and the pump cover (4) is provided with a plunger sliding chute (42) along the radial direction;

the plunger assembly (5) further comprises a plug box (52), a sliding sheet (53), a stop block (54), a first spring (55), a second spring (56) and a third spring (57), the sliding sheet (53) is slidably mounted on the outer surface of the pump cover (4), the sliding sheet (53) slides along the direction of the plunger sliding groove (42) and covers the plunger sliding groove (42) all the time in the sliding process, a plug passing hole (531) with the shape identical to that of the cross section of the plunger (51) is formed in the sliding sheet (53), the plug box (52) is mounted on the surface, deviating from the pump cover (4), of the sliding sheet (53), a bulge is formed in the middle of the plug box (52) and is sealed outwards, the plunger (51) is slidably mounted in the guide groove (521), the plunger (51) is extruded by the third spring (57) mounted in the guide groove (521) and has a tendency of propping towards the flow channel (21), and the stop block (54) is mounted at the radial central position of the outer surface of, install first spring (55) between dog (54) and stopper box (52), install second spring (56) between dog (54) and gleitbretter (53), the elastic coefficient of second spring (56) is greater than first spring (55), runner (21) are equipped with jacking boss (23) in the tip position department, the width of jacking boss (23) is less than runner (21) width, and jacking boss (23) top is close to pump cover (4) internal surface.

3. The helical reverse-curve wheel oil pump with the double ends penetrating through the shaft as claimed in claim 2, wherein: the bottom of the plunger (51) is semi-spherical, and the bottom of the flow channel (21) is semi-circular.

4. The helical reverse-curve wheel oil pump with the double ends penetrating through the shaft as claimed in claim 2, wherein: the surface of the sliding sheet (53) facing the pump cover (4) is provided with a hook block (532), and the hook block (532) is embedded into the plunger sliding groove (42) and slides along the plunger sliding groove (42).

5. The helical reverse-cam oil pump with double ends penetrating through a shaft as claimed in claim 4, wherein: the radial length of the plug box (52) taking the main shaft (1) as an axis is smaller than that of the sliding sheet (53), two ends of the sliding sheet (53) are turned outwards, and when one end, far away from the stop block (54), of the plug box (52) abuts against the turning edge of the sliding sheet (53) at the end, the bottom of the guide groove (521) is aligned with the plug hole (531).

6. The helical reverse-curve wheel oil pump with the double ends penetrating through the shaft as claimed in claim 2, wherein: helical wheel (2) are two blade structures, and end plate (20) are as central plane and both sides set up helical blade structure runner (21) and anti-bent runner (29) respectively, the spiral direction and runner (21) of anti-bent runner (29) revolve to opposite, and anti-bent runner (29) cover through another pump cover (4), and plunger (51) head direction of motion that is used for keeping apart plunger subassembly (5) of runner on anti-bent runner (29) is: radially outward when inserted into the passageway (29) and radially inward when repositioned.

Technical Field

The invention relates to the field of oil liquid conveying, in particular to a spiral reverse-curve wheel oil pump with two ends penetrating through a shaft.

Background

An oil pump is a common transportation machine, and is often used in industry to transport lubricating oil, crude oil, cooling oil, and the like, and the oil pump is a generic term, and a pump used when transporting a liquid medium other than water may be generically referred to as an oil pump.

Disclosure of Invention

The invention aims to provide a spiral reverse-curve wheel oil pump with two ends penetrating through a shaft so as to solve the problems in the prior art.

In order to achieve the purpose, the invention provides the following technical scheme:

a spiral reverse-curve wheel oil pump with two ends penetrating through a shaft comprises a main shaft, a spiral wheel, a pump shell, a pump cover and a plunger assembly, wherein the pump shell is hollow, the pump cover is arranged at one end of the pump shell, the main shaft penetrates through the pump shell and the pump cover, the spiral wheel is arranged on the main shaft, and the spiral wheel is positioned in the pump shell;

the plunger assembly comprises at least two plungers, the spiral wheel comprises an end plate and spiral blades arranged on one side of the end plate, the outer edge of the end plate is tightly attached to the inner edge face of the pump shell, one side, deviating from the end plate, of each spiral blade is opened, each spiral blade is provided with a spiral flow channel, the width of each flow channel is kept unchanged, the plungers can be inserted into the flow channels along the axial direction, the plungers are distributed at two radial circumferential angles of the spiral wheel, and media on one side of the plungers are extruded to the center or the outer edge of the spiral wheel along with the rotation of the spiral wheel after the.

The plunger piston is inserted into the flow passage to form a separation part of the flow passage, the flow passage closed by the two plunger pistons matched with the helical blade continuously flows to the central position along with the rotation of the helical wheel, the plunger piston can slide along the radial direction, a corresponding plunger piston radial sliding structure is configured, when the plunger piston reaches the middle position, the plunger piston is separated from the flow passage in a mode of pulling or jacking the plunger piston, and then the plunger piston returns to the radial far end to wait for the next period to be inserted into the flow passage again for extruding and blowing the medium. The two plungers make the spiral flow always isolated from the pump inlet, when the single-stage helical blade is adopted, the area outside the helical wheel inlet is used as the inlet area, the connection interface is arranged in the area and connected to the external oil suction pipe, and the oil medium pumped to the middle of the helical wheel is drained at the middle position of the helical wheel and used as the pump outlet. In order to keep the inlet and outlet ports isolated, the helical structure of the helical wheel should be provided with at least two turns.

Further, an impeller core opening communicated with the back surface of the spiral wheel is arranged at the end part of the flow channel, close to the central position, of the spiral wheel;

the outer edge of the end face of the pump cover is provided with an interface, and the pump cover is provided with a plunger piston chute along the radial direction;

the plunger assembly further comprises a plug box, a sliding sheet, a stop block, a first spring, a second spring and a third spring, the sliding sheet is slidably arranged on the outer surface of the pump cover, the sliding sheet slides along the direction of the plunger sliding groove and covers the plunger sliding groove all the time in the sliding process, a plug hole with the same shape as the cross section shape of the plunger is arranged on the sliding sheet, the plug box is arranged on the surface of the sliding sheet departing from the pump cover, a guide groove which is convex and closed outwards is arranged in the middle position of the plug box, the plunger is slidably arranged in the guide groove, the plunger is extruded by the third spring arranged in the guide groove and has the tendency of pushing against a flow channel, when falling from the guide groove and being inserted into the flow channel, the plunger needs to pass through the plug hole and the plunger guide groove in sequence, the bottom shape of the plunger needs to be matched with the bottom shape of the flow channel, a second spring is installed between the stop block and the sliding sheet, the elastic coefficient of the second spring is larger than that of the first spring, a jacking boss is arranged at the tail end of the flow channel, the width of the jacking boss is smaller than that of the flow channel, and the top of the jacking boss is close to the inner surface of the pump cover.

The structure gives the inlet and outlet positions of the medium and the reciprocating route and the reciprocating structure of the plunger:

the medium inlet is positioned at the interface, the medium entering the interface is filled at the outer ring position of the spiral wheel, the plunger moves inwards from the inlet of the spiral blade, new low-pressure oil is filled in the area again, the extruded oil flows outwards through the impeller core opening at the tail end of the flow channel, and the impeller core opening needs to rotate, so that the rotating impeller core opening needs to be converted into fixed-point output by using similar objects such as a gas distribution valve core for driving in the pneumatic field.

The reciprocating of the plunger is realized by the whole structure of the plunger assembly: the plunger is inserted into the flow channel and is abutted against the bottom surface of the flow channel, the plunger is taken towards the radial center along with the rotation of the spiral wheel, when the plunger reaches the jacking boss, the plunger is jacked by the jacking boss and is taken into the guide groove by the jacked plunger, the bottom of the plunger is not separated from the top surface of the jacking boss, however, the elasticity coefficient of a second spring connected with the slip sheet is larger than that of a first spring connected with the plug box, so as long as the overlapped area of the plug hole and the plunger is changed, the slip sheet can be elastically inserted between the plunger and the jacking boss, the specific arc shape at the bottom of the plunger enables the slip sheet to further push the plunger into the guide groove to be taken, after the plunger is separated from the plunger sliding groove, the plug box, the slip sheet and the plunger can simultaneously slide outwards in the radial direction to carry out the plunger resetting process, and the corresponding limit structure is arranged at the outer end of the radial position to stop the plug box at, The sliding sheet, the plunger piston, the stopped plug box and the end part of the sliding sheet are realigned to ensure that the guide groove is aligned with the plug passing hole, so that the plunger piston can be subjected to the elastic force of a third spring and has the condition of being inserted into the flow channel again, the plunger piston is inserted into the flow channel again for the flow channel isolation of the next period only when the spiral inlet position of the plunger piston reaches the lower end of the screw wheel, and the plunger piston draws a rectangular shape in space.

Furthermore, the bottom of the plunger is semi-spherical, and the bottom of the flow passage is semi-circular. The hemispherical and semi-circular trough bottoms are one set of shapes that are convenient to machine, and can also be, for example, a hat shape with a top cut off in a hemispherical shape.

Further, the gleitbretter is equipped with a hook piece on the surface towards the pump cover, and the hook piece embedding plunger spout is interior and slide along the plunger spout, and the hook piece supports when leaning on the radial outside one end of plunger spout, corresponds the radial outside one end of plunger. The hook block is used for limiting the radial outer end of the sliding sheet when hooking the plunger sliding chute. This limit structure uses the plunger spout, alleviates structure complexity.

Furthermore, the radial length of the plug box taking the main shaft as the axis is smaller than that of the sliding sheet, the two ends of the sliding sheet are tilted outwards to form flanges, and when one end, far away from the stop block, of the plug box abuts against the flanges at the end of the sliding sheet, the bottom of the guide groove is aligned with the plug hole.

The turn-ups is used for stopper box radial spacing for the gleitbretter, is in radial outer end and plunger insert behind the runner until the plunger by jacking boss jack-up moment, all is that the radial outer end of stopper box supports and leans on the radial outer end turn-ups of gleitbretter, and when the plunger reset process: namely, the plunger is jacked up by the jacking boss until the sliding sheet reaches the outer edge of the pump cover, and the radial inner end of the plug box abuts against the radial inner end of the sliding sheet.

Further, the helical wheel is the bilobed leaf structure, and the end plate sets up helical blade structure runner and anti-bent runner respectively as central plane and both sides, and anti-bent runner's spiral direction is opposite with the runner soon, and anti-bent runner covers through another pump cover, and the plunger head direction of motion that is used for keeping apart the plunger subassembly of runner on the anti-bent runner is: radially outward when inserted into the reverse curved flow passage and radially inward when reset.

By using the double-blade structure, the medium can be extruded and conveyed by the blades twice, the pressure is doubled, in addition, the core opening of the impeller at one end is directly used as the inlet of the spiral impeller at the other side, the medium flows outwards in the radial direction, the medium enters the static pump shell space outside the spiral line, the medium is pumped to the outside through the second interface on the pump cover at the side, the piston assembly at the side is blasted outwards in the radial direction, and the rectangular direction drawn by the piston is opposite to the rectangular moving direction of the piston corresponding to the spiral wheel blasted inwards in the radial direction.

Compared with the prior art, the invention has the beneficial effects that: according to the invention, a medium flow channel is constructed by the spiral wheel and the plunger, the spiral wheel drives the plunger to slide in the radial direction when rotating, the spiral wheel is jacked up by a jacking boss when approaching the main shaft and then reset on the surface of the pump cover in the radial direction, and the spiral wheel is reinserted into the flow channel for medium blowing in the next period; the medium is continuously blown, the radial inward pumping is used as the pumping flow of the main flow, a part of pressure potential energy can be pre-compressed and stored in the medium, the compression ratio can be changed by adjusting the shape of a spiral line and selecting the starting and ending positions of a specific compression channel, so that the oil pump is suitable for the characteristics of the pumped oil, and fixed-point input and output can be performed after the spiral wheels are arranged on both sides.

Drawings

In order that the present invention may be more readily and clearly understood, a more particular description of the invention briefly described above will be rendered by reference to specific embodiments that are illustrated in the appended drawings.

FIG. 1 is a first schematic view of the operation of a helical wheel according to the present invention;

FIG. 2 is a schematic view of the operation principle of the helical wheel of the present invention;

FIG. 3 is a schematic view of the plunger chute position of the present invention;

FIG. 4 is a schematic view of the media flow in a side view configuration of the present invention;

FIG. 5 is a first schematic view of the operation of the plunger assembly of the present invention;

FIG. 6 is a second schematic view of the operation of the plunger assembly of the present invention;

FIG. 7 is a third schematic view of the operation of the plunger assembly of the present invention;

FIG. 8 is a side view of the present invention with a reverse bend flow path structure;

FIG. 9 is a schematic axial view of a flow channel and a reverse-curved flow channel according to the present invention.

In the figure: the device comprises a main shaft 1, a spiral wheel 2, an end plate 20, a flow channel 21, an impeller core opening 22, a jacking boss 23, a reverse-curved flow channel 29, a pump shell 3, a pump cover 4, a connector 41, a plunger sliding groove 42, a plunger sliding groove 49, a second connector 5, a plunger assembly 51, a plunger box 52, a guide groove 521, a sliding sheet 53, a plug hole 531, a hook block 532, a block 54, a first spring 55, a second spring 56 and a third spring 57.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. 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.

As shown in fig. 1 to 4, the spiral reverse-bending wheel oil pump with two ends penetrating through a shaft comprises a main shaft 1, a spiral wheel 2, a pump shell 3, a pump cover 4 and a plunger assembly 5, wherein the pump shell 3 is hollow, the pump cover 4 is installed at one end of the pump shell 3, the main shaft 1 penetrates through the pump shell 3 and the pump cover 4, the spiral wheel 2 is installed on the main shaft 1, and the spiral wheel 2 is located in the pump shell 3;

plunger subassembly 5 includes two at least plungers 51, and helical wheel 2 includes end plate 20 and sets up the helical blade in end plate one side, and 3 inner fringe faces of pump case are hugged closely to end plate 20 outer fringe, and one side that the helical blade deviates from end plate 20 is opened, and helical blade constructs spiral flow channel 21, and flow channel 21 width remains unchanged, and the helix is the equidistance helix promptly, under the polar coordinate system: expressed mathematically as ρ (t) = a × t + b, where a and b are constants, t is an independent variable, ρ is a polar radius, the plunger 51 can be inserted into the flow channel 21 in the axial direction, the plungers 51 are distributed at two radial circumferential angles of the screw wheel 2, and the plunger 51 pushes the medium on the side of the plunger 51 toward the center or the outer edge of the screw wheel 2 as the screw wheel 2 rotates after the plunger 51 is inserted into the flow channel 21.

The plunger 51 is inserted into the flow channel 21 to form a separation part of the flow channel, the flow channel closed by the two plungers and the helical blade continuously flows to the central position along with the rotation of the helical wheel 2, the plunger 51 can slide along the radial direction, the corresponding radial sliding structure of the plunger 51 is configured, when the plunger 51 reaches the middle position, the plunger 51 is separated from the flow channel 21 by pulling or jacking the plunger 51, and then the plunger 51 is re-inserted into the flow channel 21 to extrude and blow the medium when the plunger 51 returns to the radial far end to wait for the next period. The two plungers 51 always isolate the spiral flow from the inlet of the pump, when the screw blade is single-stage, the area outside the inlet of the screw wheel 2 is used as the inlet area, the connection interface is arranged in the area and connected to an external oil suction pipe, and the oil medium pumped to the middle of the screw wheel 2 is drained at the middle position of the screw wheel 2 and used as the outlet of the pump. In order to keep the inlet and outlet ports isolated, the helical structure of the helical wheel should be provided with at least two turns.

Although the width of the flow channel is kept unchanged, when the flow channel rotates and moves inwards in the radial direction, the volume of a medium wrapped between the two plungers 51 can be reduced, the compressibility of oil is small, but the compressibility is about 1%, when trace gas is mixed in the oil, the compressibility is larger, and the compressibility is also a reason for the fact that a plurality of gear oil pumps cannot work stably.

As shown in fig. 1 to 7, an impeller core opening 22 communicated with the back surface of the helical wheel 2 is arranged at the end part of the flow channel 21 at the position of the helical wheel 2 close to the center;

the outer edge of the end face of the pump cover 4 is provided with a connector 41, and the pump cover 4 is provided with a plunger sliding chute 42 along the radial direction;

the plunger assembly 5 further comprises a plug box 52, a sliding sheet 53, a stop block 54, a first spring 55, a second spring 56 and a third spring 57, the sliding sheet 53 is slidably mounted on the outer surface of the pump cover 4, the sliding sheet 53 slides along the direction of the plunger sliding groove 42 and always covers the plunger sliding groove 42 in the sliding process, the sliding sheet 53 is provided with a plug through hole 531 with the same shape as the cross section of the plunger 51, the plug box 52 is mounted on the surface of the sliding sheet 53 departing from the pump cover 4, the middle position of the plug box 52 is provided with a guide groove 521 which is convex and closed outwards, the plunger 51 is slidably mounted in the guide groove 521, the plunger 51 is extruded by the third spring 57 mounted in the guide groove 521 and has the tendency of propping against the flow channel 21, when the plunger 51 falls from the guide groove 521 and is inserted into the flow channel 21, the plug needs to sequentially pass through the plug through hole 531 and the plunger, the stop block 54 is arranged at the radial central position of the outer surface of the pump cover 4, the first spring 55 is arranged between the stop block 54 and the plug box 52, the second spring 56 is arranged between the stop block 54 and the sliding sheet 53, the elastic coefficient of the second spring 56 is greater than that of the first spring 55, the lifting boss 23 is arranged at the tail end of the flow passage 21, the width of the lifting boss 23 is smaller than that of the flow passage 21, and the top of the lifting boss 23 is close to the inner surface of the pump cover 4.

In the following discussion, it is often necessary to describe both ends of the plunger slide groove 42, and therefore, since the plunger slide groove 42 is extended radially, one end thereof away from the main shaft 1 is referred to as a radially outer end, one end thereof close to the main shaft 1 is referred to as a radially inner end, and the radially outer end and the radially inner end of the remaining components have the same meaning.

The structure gives the positions of the inlet and the outlet of the medium and the reciprocating route and the reciprocating structure of the plunger 51:

the medium inlet of the invention is located at the interface 41, the medium entering at the interface 41 is filled at the outer ring position of the spiral wheel 2, the plunger 51 moves inwards from the inlet of the spiral blade, new low-pressure oil is filled in the area again, the extruded oil passes through the impeller core opening 22 outwards at the tail end of the flow channel 21, and the impeller core opening 22 needs to rotate, so that the rotating impeller core opening 22 needs to be converted into fixed-point output by using a gas distribution valve core and other similar objects used for driving in the pneumatic field, of course, another structural mode can be provided in the embodiment, and the effect of fixed-point output can also be achieved.

The reciprocation of the plunger 51 is realized by the overall structure of the plunger assembly 5: as shown in fig. 5, the plunger 51 is inserted into the flow channel 21 and abutted against the bottom surface of the flow channel, the plunger 51 is brought to the radial center with the rotation of the screw wheel 2, when it reaches the lift boss 23, the plunger 51 is lifted by the lift boss 23, the lifted plunger 51 is received in the guide groove 521, the bottom of the plunger 51 is not separated from the top surface of the lift boss 23, however, since the second spring 56 connected with the slide piece 53 has a larger elastic coefficient than the first spring 55 connected with the plug box 52, as long as there is a change in the overlapping area of the outline of the plug box 52 and the plunger 51, the slide piece 53 is elastically inserted between the plunger 51 and the lift boss 23, the specific circular arc shape of the bottom of the plunger 51 causes the slide piece 53 to further push the plunger 51 into the guide groove 521 to be received, and the plug box 52, the slide piece 53 and the plunger 51 slide radially outward together after the plunger 51 is separated from the plunger slide groove 42, and in the process of plunger resetting, the corresponding limiting structures are arranged at the outer ends of the radial positions, so that the plug box 52, the sliding sheet 53 and the plunger 51 can be stopped at a certain position, the ends of the stopped plug box 52 and the stopped sliding sheet 53 are realigned to ensure that the guide groove 521 is aligned with the through plug hole 531, the plunger 51 can be subjected to the elastic force of the third spring 57 to have the condition of being inserted into the flow channel again, the plunger is inserted into the flow channel 21 again to perform the separation of the flow channel 21 in the next period only when the spiral inlet position of the screw wheel 2 reaches the lower end of the plunger 51, and the plunger 51 draws a rectangular shape in space.

As shown in fig. 7, the bottom of the plunger 51 is semi-spherical, and the bottom of the flow passage 21 is semi-circular. The hemispherical and semi-circular trough bottoms are one set of shapes that are convenient to machine, and can also be, for example, a hat shape with a top cut off in a hemispherical shape.

As shown in fig. 7, a hook 532 is disposed on a surface of the slide plate 53 facing the pump cover 4, the hook 532 is embedded in the plunger slide groove 42 and slides along the plunger slide groove 42, and when the hook 532 abuts against a radially outer end of the plunger slide groove 42, the radially outer end of the plunger 51 is corresponding to the hook 532. The hook 532 serves as a stop for the radially outer end of the slide 53 when hooking the plunger slide groove 42. This limit structure uses plunger spout 42, alleviates structure complexity.

As shown in fig. 5 to 7, the radial length of the plug box 52 with the spindle 1 as the axis is smaller than that of the sliding sheet 53, two ends of the sliding sheet 53 are turned outwards, and when one end of the plug box 52 away from the stopper 54 abuts against the turned edge of the sliding sheet 53 at the end, the bottom of the guide groove 521 is aligned with the plug passing hole 531.

The flanging is used for radial limiting of the plug box 52 relative to the sliding sheet 53, when the plunger 51 is at the radial outer end and the plunger 51 is inserted into the flow channel 21 until the plunger 51 is jacked up by the jacking boss 23, the radial outer end of the plug box 52 abuts against the radial outer end flanging of the sliding sheet 53, and when the plunger 51 is in the resetting process: that is, after the plunger 51 is jacked up by the jacking boss 23 until the slide sheet 53 reaches the outer edge of the pump cover 4, the radially inner end of the plug box 52 abuts against the radially inner end of the slide sheet 53.

As shown in fig. 8 and 9, the spiral wheel 2 is of a double-blade structure, the end plate 20 is used as a central plane, and the spiral blade structure flow passage 21 and the recurve flow passage 29 are respectively arranged on both sides, the spiral direction of the recurve flow passage 29 is opposite to the spiral direction of the flow passage 21, the recurve flow passage 29 is covered by the other pump cover 4, and the head part of the plunger 51 of the plunger assembly 5 for isolating the flow passage on the recurve flow passage 29 moves in the following direction: radially outward when inserted into the recurved canal 29 and radially inward when repositioned.

With the double-blade structure, the medium can be extruded and conveyed twice by the blades, the pressure is doubled, and the impeller core port 22 at one end is directly used as the inlet of the spiral impeller at the other side, and the medium flows radially outwards, enters the space of the stationary pump shell 3 outside the spiral line, and is pumped outwards through the second port 49 on the pump cover 4 at the side, and the direction of the rectangle drawn by the plunger 51 of the plunger assembly 5 at the radially outwards-blowing side is opposite to the direction of the rectangular movement of the plunger 51 corresponding to the spiral impeller 2 which is blown radially inwards, and is shown by two closed chain dotted rectangles in fig. 8.

It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof. The present embodiments are therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.