JPS5827894A - Fluid pump having electromotor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fluid handling device, and more particularly, to a magnetic drive device using a positive displacement pump driven to handle a fluid. .

In order to prevent contamination of the fluid being handled, some pumps are known which have an electric motor and a rotor shaft driven by the electric motor and having a joint consisting of two groups of permanent magnets. One group of permanent magnets is attached to the shaft of an electric motor and rotates with the motor, and the other group of permanent magnets is attached to the shaft of a rotor and rotates with the rotor.

In such types of pumps, the interior of the pump is sealed by a non-magnetic diaphragm placed between two groups of permanent magnets to prevent contamination from the product term. The rotor shaft is generally connected to the pump device.

US Pat. No. 2,970,548 discloses a magnetically driven centrifugal pump. The rotor shaft of the pump is connected to the motor by two permanent magnets: one fixed to the motor shaft and another permanent magnet coaxially fixed to the rotor shaft. Ru. Other examples of centrifugal pumps with coaxially arranged magnetic drives are disclosed in US Pat. Nos. 3,205,827 and 3,238,888. One disadvantage of permanent magnets that are coaxially arranged is that the walls of the diaphragm are connected to the metal sheets back-to-back.
11111 This is something that must be done. However, the melting of the thin edges of the metal sheet! In this case, it is difficult to obtain a satisfactory seam.

Furthermore, it is difficult to make a cylindrical wall with accurate dimensions and accurate shape so that the diacrum wall is flush with the boundary box near one stator. Considering this, the air gap between coaxially arranged permanent magnets must be sufficiently wider than the air gap between comparable axially arranged permanent magnets. The wide gaps between the coaxially arranged permanent magnets increase the loss of magnetic flux through the gaps, resulting in a corresponding decrease in performance, and the diameter of the components must be increased to transmit higher torques. Must be IK.

U.S. Pat. No. 2,996,994 discloses a pump driven by a round submersible electric motor that pumps liquid fuel using permanent magnets spaced apart in the axial direction of the tank. The pump is driven by an inter-stub motor through a magnetic coupling that operates between the walls of the motor housing. This type of pump is suitable for use in various fuel tanks. The driving member and driven member of the magnetic coupling are arranged in the pattern of the wall in which the hole is drilled. The hole functions as a hard diaphragm between the two magnets. The drive member and the driven member are therefore separated by an axial gap. Another example of an axial air gap motor for use in centrifugal pumps is U.S. Pat. No. 3,223,040.
No.8 Kl#! It is shown.

Centrifugal pumps have several drawbacks. 1K Pumps of this type are inherently high speed devices and are more efficient when handling fluids with high flow rates and low pressure rises; therefore, they are less efficient at low flow rates and high pressure rises. Second
In addition, the pressure increase generated by centrifugal pumps is directly proportional to the square of the speed, so centrifugal pumps do not produce high pressure increases at low speeds. M3, centrifugal pumps are prone to cavities and thus lose their superior properties. When any of these conditions occur, the centrifugal pump ceases to pump, resulting in heat generation, noise, and vibration, which shortens the life of the pump.

Another improvement to a pump having axially spaced magnets is disclosed in U.S. Pat. No. 3,470,824. In the U.S. patent, an electrically operated monitor is sealed from the pump chamber and transmits rotational driving force to a pump impeller within the pump chamber. One pump has sliding vanes in a fixed casing so that the liquid can be moved 1 m without the need to apply centrifugal force.

One major drawback of rotary positive displacement pumps is that their efficiency depends on the mechanical clearance of the rotating member O. Of course, the actual clearance is a function of machining and assembly operations. In addition, in the case of low viscosity liquids, it is necessary to have very high machining accuracy and assembly precision so as to reduce the risk of liquid leakage through the pump gap. The size of the blade depends on several factors. Generally, the wider the gap, the larger the bevel. Since the tip of a double-impeller is susceptible to wear, and the blades must be replaced frequently, pumps with double-impellers cannot be used for pumping low-viscosity liquids. 9. Such rotary blade rotary positive displacement pumps are complex, have large friction losses, are expensive to manufacture, and are unable to cut off excessive pressure when applied to the liquid they are handling.

Therefore, any of the above-mentioned centrifugal pumps and vane pumps can produce 1 fuel *! when the pump and the electric motor are connected by a magnetic drive coupling. 7.It is not an appropriate pump to handle. Also, none of these pumps are simple, expensive to manufacture, and do not have overpressure means to limit the discharge pressure of the fluid being handled. Up to 1kK, all of these pumps are unsuitable for many fluids including fuel, do not produce high pressures at low speeds and pressures, are prone to cavitation, are cumbersome to assemble, and have low efficiency.

The present invention is directed to a pump with an axially gapped motor for driving a positive displacement gainer zero pump ('rd@r pHlaν) which produces a positive pressure rise at the inlet. , to the gerotor pump,
High pump efficiency is achieved without the high friction and wear found in conventional pumps. This pump has a simple structure and is suitable for obtaining the required manufacturing clearance at low cost. Furthermore, the present invention allows for the use of wide axial gaps in pump assembly without reducing pump efficiency or increasing manufacturing costs. The pump of the invention is suitable for pumping fluids of various viscosities. Finally, the axial gap rotor pump is designed to prevent contamination of the fluid pumped therewith and to facilitate the delivery pressure of the fluid pumped thereto.

The pump includes a housing having a chamber having one end and an opposite end. A die tube main member is provided within the chamber and divides the interior of the chamber into a first interior portion adjacent one end and a second interior portion adjacent the other end. A first shaft is rotatably provided within the first inner portion of the chamber. A diaphragm section KIiI&L is attached to one end of this shaft, and an electric motor for rotating the shaft is attached to the other end. A second shaft is rotatably pitched into the second inner portion of the chamber. One end of this second shaft is a diaphragm member K11l.
Abutting and opposite the end of the building 1 is a second end. The magnetic drive member is secured such that a portion of one end of the first shaft adjacent the diaphragm member is allowed to slide but not rotate. A magnetically driven member is secured to the first end of the second shaft near the diaphragm member. In response to a magnetic attraction force exerted between the magnetically driven member and the magnetically driven member via the diaphragm member,
The magnetically driven member rotates with the magnetically driven member. Finally, the gerotor attached to the other end of the second shaft
The pump member pumps fluid when the second shaft is rotated.

It is therefore an object of the present invention to provide a fluid pump connected to an axial magnetic coupling via a non-magnetic diaphragm member connected to a gerotor pump having an overpressure limiter at the outlet.

Gerotor pumps are designed to safely handle low viscosity fluids with high pump efficiency. Finally, gerotor pumps produce a positive pressure rise at the inlet, have an automatic priming function (s@lf-prlmtag), can deliver a wide variety of @tV fluids, and rely on fluid friction within the pump to This reduces losses and increases pump efficiency.

Hereinafter, the present invention will be described in detail with reference to the drawings.

Illustrated in the figure is a positive displacement magnetically driven gerotor pump 100 according to the present invention. This pump 1 OK is one end 1
A housing 1° is provided having a housing 2 and an opposite end 1.

The housing IOK is formed with a chamber 2°. A main body member SO is fixed to the inner portion 1111 of the housing 10 by suitable means such as welding, and divides the chamber 20 into a first inner portion 22 and an opposite second inner portion 211 . A first inner portion 22 is formed adjacent one end 12 of housing 10 . The second inner portion is formed as the other end 1!11.KII* of the housing 10. A pair of bearings 3 are disposed inside the twentieth inner portion 22 of the housing 190.
2.34 is installed. One end of the bearing 32 is 12K.
li*, and the other bearing 34 is provided in contact with the diaphragm member 5OKII.

The drive shaft 4s extending on both sides of the armature 420 of the electric motor 40 is rotatably supported by the bearings 32 and 34. A motor magnet 44 and a field winding (not shown) are coaxial with the armature 42 and mounted on the inner surface 24 of the first inner portion 22 of the chamber 200. An electric commutator 114g1 is provided adjacent to the bearing 32. One end 12
An electrical contact 14 is connected to a power source (not shown) through the
kl [number of pushshi s2 connected and stone. Current commutator 46
The pusher 52 is connected to the commutator 41 so that the armature 42 is
KI! I am made to touch it. The field winding is electrically connected to IE (not shown) via electrical contacts (El not shown). By appropriately changing the electrical components of the motor, it is possible to use either DC power or AC power as a stain source. Here λ
It is not necessary to drive the pump with an electric motor when carrying out the present invention, and it is possible to appropriately change the parts used.]
It will be appreciated by those skilled in the art that a hydraulic motor can be used with an air motor.

Ninth 1 diaphragm member io#i for the purpose to be explained later
Made of non-magnetic material. This diaphragm member sO includes a first inner portion 22 and a twentieth inner portion 28 of the chamber 20.
A fluid seal is also configured to prevent fluid from leaking between zero and zero.

A first thrust button or washer s6 is provided between one end 4I of the drive shaft 4- and the diaphragm #sOO. One end 4- of the drive shaft 411 is the diaphragm member S.
・Washer S6 Hiro Diaphragm 5 parts to prevent the diaphragm 5 part #SO from wearing out! !
@Km I am made to touch it.

A ring-shaped magnetic drive member 6 is disposed on the drive shaft 4, 4, and 4s in close proximity to the first thrust washer 56.

A plurality of flats 6 provided on the inner surface of the magnetic drive member 60
2 and a plurality of 7 bolts attached to the drive shaft 48)
47], the magnetic drive member 60 can slide axially over the drive shaft 48. Therefore, the magnetic drive member 60 can slide axially along the drive shaft 48 to compensate for manufacturing tolerances and wear of the first thrust washer 56 as needed. The magnetic drive member 60 has a ring-shaped backing material 64 made of a suitable magnetically permeable material, preferably steel. A permanent magnet 66, which is a two-mic permanent magnet, is formed in an 8-pole configuration and is adjacent to the first thrust washer 56, but is not connected to the diaphragm member 5.
0 and is appropriately shifted to the backing member 64. Therefore, the diaphragm member 5
A gap 65 exists between the ring-shaped magnetic drive member 60 and the annular magnetic drive member 60 . This gap changes somewhat as the washer 58 wears.

Inside the second inner part 28 of the chamber 20 a pair of bearings ss, ss is arranged. A driven shaft 78 is supported by these bearings 3@, $11. The first end 82 of this driven shaft, that is, the second shaft 78 is connected to the diameter 7? Mum member 5 (l
The second end of the second shaft is supported by a bearing 36 in close proximity to the bearing 36, and the second end of the second shaft is supported by a bearing 38 in proximity to the other end 18 of the housing 10. 18 and the diaphragm member 50
A second thrust button or thrust washer sll is provided between 0 and 0. A second thrust button or thrust washer 5$ is brought into contact with one diaphragm member 50 so that the first end 82 of the second shaft 78 does not rub and wear against the diaphragm member 50.

The magnetic driven member TO rotates on the 20th axis T@ and and 4.
is fixed to the second shaft 711. The magnetically driven member TO has an annular backing member 74 made of a suitable magnetically permeable material, preferably steel. An 8-pole permanent magnet T6 is separated from the washer S by a predetermined distance O and is connected to the diaphragm member s.
◎Diaphragm member so
Those skilled in the art will appreciate that any equal number of permanent magnets can be used to magnetically couple the magnetically driven member. However, it is important that the diaphragm member 5001 permanent magnets@6 are aligned with the corresponding one permanent magnet 7@ of the magnetically driven member 70. By doing this, the air H@S and the diaphragm member 50 come out from one permanent magnet @6. IIIC) Permanent magnet 116 is always aligned with permanent magnet 711, and the diamond 7 member i
When one of the magnetically driven member 70 and the magnetically driven member 70 is rotated relative to the other, there is no interference between the two. The spacing between permanent magnets 1 and T6 occurs when a force greater than the magnetic attraction between the permanent magnets is applied, such as when the pump is prevented from rotating.

A rotor pump sO is mounted on the second shaft 71 near the second end 4. Jin's Grotor Pump 9
0 is a ring-shaped pack grate member 8 and an inlet ring-shaped member 8!
1, 3 positive displacement members, namely male rotor gear I2
, an annular female member 94, and an outer annular member s6 (FIGS. 3 and 5).

An annular backplate member 86 is connected to the inner surface of the second inner portion. One surface of the back plate member $6 is provided near the driven member 700, and two kidney-shaped openings mrs and io are formed facing each other on the other surface. The 20th axis I4 extends along the inner surface of the back plate member lI6. penetrate. The three members 92, @4, 96U are respectively arranged centrally with respect to the axis of the second shaft 84 so as to contact the annular back plate member 116. The male rotor gear 92 is set coaxially with the second shaft so that it can slide axially but not rotate. The ring-shaped female gear member 94 meshes with the Hiroo rotor gear 92K.

Another outer annular member 96 is inserted into the inner part 211 of the second inner part 2 of the chamber 20. Ninth, for the purposes of his explanation, the outer ring member ■60 inner m5ra is eccentrically centered by a predetermined radial distance from the vertical axis @■ passing through the center line of the outer surface 88 of the outer ring member s6. 94 Hirogai individual ring-shaped member! It is fitted into I6 so as to face the inner m117 of the outer ring member 116 of the one-ring electric gear member s4. In this case, the diameter of the outer surface s5 is made slightly smaller than the diameter of the inner surface 97 so that a slight diametrical gap is created between the outer surface s5 and the inner surface 1ITO. This diametrical gap allows the female W* wheel member s4 to float within the outer annular member 96.

The annular AM gear member $4 has an annular inner tooth profile surface 83.

The number of teeth formed on the annular inner tooth profile is one more than the number of teeth formed on the male rotor gear 12.

The male rotor gear II 2@2 rotates concentrically about its axis 18. The teeth 11 of the male rotor gear s2 are aligned with the inner tooth profile surface 93K of the female gear member 94 so that the male rotor gear s2 and the 1IAffi gear member 94 rotate in the same direction.
interlock. However, the male rotor gear 82 advances by one tooth each revolution. When the female gear 1 member 94 rotates together with the male rotor gear s2, the outer annular member s@O inner surface 17
Since the teeth are eccentric by a radial distance, the teeth engage with each other by a distance of 9, and are separated by a distance of 9.

A gator pump 90 is provided between the backplate member $6 and the inlet member sI. The inlet member is provided with a kidney deployment port 7,118 which functions as an inlet opening and an outlet opening, respectively, for the health housing 10. Each kidney deployment port 87°aa#'i is axially aligned with each kidney deployment port of the annular back plate member 86. The inlet ring housing 10 is slidably arranged on the inner surface of the second inner portion of the housing 10. A rounding which prevents this inlet member from rotating together with the grouter pump-O is provided within the inner part of the 20th inner part of the inlet member housing 1o.

One kidney deployment opening 81 is located in the upper half of the inlet member Is, and the second kidney deployment opening $8 is located in the upper half of the entrance member 8s.
(Figure 4).

In addition, 1
These parts are connected to each other by at least two bins 4.

As mentioned above, the outer ring member has an inner surface sT that is eccentric a distance with respect to a horizontal diametrical axis 99 passing through the centerline of the outer surface iIs. This distance is the upper half 85 of the entrance member 8s.
located along the diametrical axis 11 dividing the lower half 83 from the lower half 83.

The inlet port 2 is formed in an end plate member 14 which is attached to the other end of the housing 10 so as to connect the inlet port 2 to the inlet kidney-shaped member 8T and transmit the flow to that member. Similarly, the outlet boat 6 is connected to the kidney-shaped member row so that the flow can be transmitted to the member 1 housing 100.
A robot 6 is formed from the end plate member 141'C which is attached to the other end 1BK. When the gelter pump @O is rotated, the fluid sent by the pump is discharged into the space between the rotor gear member s2 and the female gear member ■4 due to the engagement and disengagement of the teeth. Ru. The inlet boat 2 thus constitutes an inlet fluid passageway which is connected to the pumping fluid by means of suitable conduits. Outlet port 6 is connected by suitable conduit to a container (not shown) that receives pressurized fluid from pump 100. A one-way fluid flow mechanism 8, such as a conventional check valve, is provided to flow fluid in one direction from the gerotor pump through the outlet boat 6 and
It functions to release the fluid therein when the bong 100 is stopped.

The efficiency of any field pump, such as that described herein, depends on the axial clearance of the components.

Three members 112, 114 of the game coupon. Inlet member-9 is biased toward the gerrotor pump to minimize the gap between H. For this purpose, a pair of O cavities T2 are formed which are separated by the inlet member 81 proximate the other end 18 of the housing 10. Each cavity T2 is covered with an elastic member I8. The resilient member, in the embodiment described herein, is a spring biased member, such as a helical spring. The resilient member 68 connects the inlet ring to the gerotor pump member 112. ml 4.111
1, those members 112.84.9
6 and the inlet ring member 89 and the backing plate member 8
Minimize the axial clearance between 6 and 6.

Next, the operation of this pump will be explained.

When the electric motor 40 is connected to a power source (not shown), the pump 10
0 is activated.

As the motor rotates, fluid is drawn through the inlet boat 2, which is connected to the inlet kidney-shaped opening 8T. When the male rotor gear 92 meshes with the female gear member 94K,
Fluid is drawn into female gear member 94 and kidney-shaped cavity 79 while at the same time causing female gear member 94 and kidney-shaped cavity 80
It is pushed out through the kidney-shaped opening 88 and into the exit boat 6.

The interlocking action of the pm rotor gear 92 and the inner annular tooth profile 93 of the female gear member 94 as they rotate creates a series of alternating expansion and contraction chambers therebetween. This action causes fluid to be actively moved when fluid is in communication between the pump and the appropriate inlet and outlet boats. The male rotor gear and the female gear member are in a conjugate relationship and are in continuous fluid contact during the contouring operation. Therefore, when the inner member rotates once, the male rotor gear has a conjugate relationship with the mW gear member. It is K to move forward by one tooth. The amount of fluid displaced in one rotation is proportional to the size of the fine rotor gear, the eccentric distance to the M gear member, and the thickness of the pump. Therefore, gear members 92, 114
When the members rotate relative to each other, fluid flows between the members 92 and 94.
This pump 100 exhibits a good discharge characteristic because the pump 100 is drawn into the uninterlocked space between
T) The magnetic drive member 60 is rotated via 60.47. As mentioned above, this magnetic drive member 60 is attached to the shaft 48.
Since it is attached to the shaft 4 so as to slide in the longitudinal direction, even if the axial position of the motor's armature changes, the frictional pressure exerted by this driving member 60 on the diaphragm 50 changes. do not. The magnetic force of the magnetically driven member 600 is transmitted to the magnetically driven member TO via the air gap 65, the diaphragm member 50, and the air ays. This member To can freely rotate on the axis T8. A second thrust washer 58 prevents driven shaft T8 from rubbing against diaphragm 50. Therefore, when the driving member 60 is rotated by the electric motor, the driving member 60 always rotates the driven member To.

When a pressure higher than the desired value develops in the pump outlet opening 88, the inlet member 89 moves to the grouter pump member 92.
．． 94 in the axial direction. The member @1 is
Pushing the biasing member 6@ toward the other end 18 of the pump O
As a result, the members 92, 94° move axially away from the member 94°sO. The pumped fluid can then flow from the outlet kidney-shaped port 88 to the inlet kidney-shaped port 8T, thereby reducing the pressure of the pumping fluid. The degree of deflection by the four-fold member 68 can be varied to match the highest desired discharge pressure to be generated (by the pump 100K).

It will be appreciated that the pumps described above can be used to pump fluids of high viscosity 4 as well as fluids of low viscosity. Furthermore,
When debris or other foreign material is drawn into the pump members 12, 114 during running, the pump operation is stopped and the grouter pump is prevented from rotating 1!00 times.

[Brief explanation of the drawing]

Figure 1 is a partial cross-sectional view of the magnetic pump of the present invention, Figure 2 is a cross-sectional view of the grouter pump of the present invention taken along line 2-211 in Figure 1, and Figure 3 is a cross-sectional view taken along line 3-31iK in Figure 1. 4 is a sectional view taken along line 4--4 in FIG. 1, and FIG. 5 is an exploded perspective view of the grotor pump. 10...and housing, 20...chamber, 50
...Diaphragm member, 60...Magnetic drive member, 66...Permanent magnet, To...Magnetic driven member,
sO...Grotor pump, 86...Back plate member. Tokuken Applicant: 7 Asset Enterprises, Inc. Agent: Masa Yamayo IN (and 1 other person)

Claims (1)

[Scope of Claims] (1) A housing having a chamber having one end and an opposite end, and a first inner surface fixedly attached to the interior of the chamber and adjacent to the one end. a diaphragm member configured to be rotatably arranged in the tenth inner portion O and proximate the diaphragm member; Do 1
a first ring having an eleventh end and a twentieth end opposite the first end; - a first ring rotatably mounted within said twentieth inner portion of said chamber; , a second shaft having an end proximate a diaphragm member @1 and a second end opposite the first end; and a second shaft proximate the diaphragm member. a magnetic drive element mounted on said one end so as to be able to slide but not rotate, and a magnetically driven element for pumping fluid when said second shaft is rotated. a gerotor pump element fixed to a second shaft; and rotating the magnetically driven element with the magnetically driven element in response to an attractive force exerted between the magnetically driven element and the magnetically driven element. 1. A fluid pump having an electric motor, characterized in that the magnetically driven element is fixed near the diaphragm member at the end of the shaft. (2. A fluid pump as claimed in claim 1, wherein the getter pump element is defined within the second inner portion of the chamber and is connected to the magnetically driven member. an annular pack plate member having a proximate surface and an opposite surface; a device disposed within the second interior portion of the chamber proximate the opposite surface of the housing; an inlet annular member disposed between the annular plate member and the inlet annular member to ensure fluid movement and fluid flow in response to rotation of the second shaft; 3. A fluid pump according to claim 2, characterized in that the positive displacement element comprises: A male!!1 rotor gear fixed to the shaft of No. 2, a wing-shaped female lIi!-wheel member that cooperates and meshes with this male rotor gear, and a plow lid gear member o)+5 arranged around (4) The fluid pump according to claim 80, wherein the outer annular member has an inner diameter and an outer diameter. having an inner diameter a predetermined radial distance from a longitudinal axis passing through said outer diameter.
A fluid pump characterized in that it is eccentric. (5) Il! 8. The fluid pump according to claim 8, wherein the annular back plate member is connected to the outer annular member by the inlet annular member, and the annular back plate member is connected to the outer annular member by the inlet annular member. A fluid pump characterized in that the member is prevented from relative movement with respect to the inlet annular member. (6) The fluid pump according to claim 1, further comprising an inlet boat that is connected to the other end of the housing, and the fluid pump is configured to supply fluid to the getter pump. A fluid pump, characterized in that it is coupled to a gerotor pump for supplying a fluid to a gerotor pump. (7) An OR body pump as set forth in claim om8o paragraph 1, wherein the chamber hole is mounted near the input port for receiving fluid from the gerotor pump. A fluid pump that is connected to a gelator pump. (8) Second claim. ! In the OR body pump described in JK, the annular pack grate member O Zeng has a pair of kidney m-shaped faces facing each other and separated from each other on the opposite side! A fluid pump characterized by having a protrusion that forms two levels. (9) The fluid pump according to claim 2, wherein the inlet annular member is located at the other end of the housing.
Face the 1st C1 box that touches $KIli and this -l side! 120 sides, the 20th side having a protrusion defining a pair of kidney-shaped openings facing each other and spaced apart. (2) The fluid pump according to claim 2, wherein the housing is arranged between the other end and the inlet annular member;
The fluid pump further comprises an element for reducing the axial gap therebetween. CIIJ% Claim 80. The fluid pump of claim 7, wherein the outlet boat further has a check valve disposed therein to prevent fluid flow to the gerotor pump. A fluid pump characterized by: a housing having a chamber having one end and the other end; a first shaft which is fitted with a V (V) for rotation in the chamber and on which the electric motor is mounted; a second glaze mounted in such a way that it can be rotated near the axis of a the diaphragm member KIII on the first shaft;
a drive member slidably mounted on the second shaft adjacent to the diaphragm member; a driven member slidably mounted on the second shaft adjacent to the diaphragm member; The five diaphragm members Kl can touch and slide on the one end 11 of the shaft of the diaphragm,
a magnetic drive member fixed to the first end of the second shaft near the diaphragm member; a gerotor pump element secured to the second end of the 20th shaft, the gerotor pump element pumping fluid in response to rotation of the 20th shaft; a plurality of wedge-shaped magnets disposed at the ends of the annular member, each of the plurality of wedge-shaped magnets having a north pole and a south pole; One of the magnets is arranged with a narrow gap in the radial direction from each of the other magnets, and the north pole of each of the magnets is further attached to the south pole of each of the other magnets. Pump with. Q: 1411 The pump according to claim 111112, wherein the gerotor pump element has a surface opposite to the magnetically driven member IIC adjacent 10 boxes, and an annular back plate defined within a second inner portion of the chamber; an inlet annular member disposed adjacent the other end of the housing in the second inner portion of the chamber; a volumetric element disposed between the annular back plate member and the inlet annular member to ensure fluid movement and fluid flow in response to rotation of the inlet annular member; A pump according to claim 13, characterized in that the displacement element is fixed to the shaft of its shaft 2 in order to rotate with the second shaft. It is characterized by further comprising: a male rotor gear, a ring-shaped female W* wheel member that meshes with the ini+rotor gear k, and an external ring-shaped member disposed around the ring-shaped 111I!1IlllI wheel member. Fluid pump (O fluid pump according to claim 14, wherein the outer annular member has an inner diameter and an outer diameter, and the inner diameter is such that the outer diameter is at a predetermined radial distance from the longitudinal axis of the stone passage. #1 body pump according to claim 14, wherein the annular pack plate member is eccentrically disposed between the outer annular member and the inlet annular member. A fluid pump characterized in that the annular backplate member is coupled to a member by a bottle to prevent relative movement of the annular backplate member with respect to the outer annular member and the inlet annular member. 13. The fluid pump of claim 12, wherein the housing further comprises an inlet boat fastened to the other end, the inlet boat being connected to the gerotor pump element for supplying fluid to the gerotor pump element. 80. A fluid pump according to claim 12, characterized in that the fluid pump is connected to the gerotor pump element in fluid communication with the pump element, wherein the chamber is connected to the gerotor pump element in fluid communication with the pump element. further comprising an outlet port disposed at an end proximate to the inlet port, the outlet port having a port for receiving fluid from the gelter pump element; A fluid pump as claimed in claim 13, characterized in that the annular backplate member is connected to its opposite gerotor pump element. 14. A fluid pump according to claim 13, characterized in that the side surfaces have protrusions forming a pair of kidney-shaped cavities facing each other and spaced apart, the inlet annular The member has a first surface adjacent to the other end of the housing, and a second surface facing the first surface, and the second surface has a pair of kidneys facing each other and separated from each other. A fluid pump characterized in that it has a protrusion forming a shaped cavity on its second side. 14. A fluid pump as claimed in claim 13, wherein the housing is arranged such that the housing extends toward the positive displacement element and the annular backing plate member between the other end and the inlet annular member. 20 with the annular backing member and the volume l! A fluid pump further comprising an element for narrowing an axial gap between the element and the inlet annular member. 01% Eave A fluid pump according to claim 18*, characterized in that a check valve is provided in the outlet boat to prevent the flow of fluid to the gerotor pump element. fluid pump.