JP2005113876A - Flat plate type pump device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a mechanism smoothly transmitting torque from a shaft to a gear. <P>SOLUTION: This pump device is equipped with a casing (3) inside which a flow passage of fluid communicating a suction port (48) with a discharge port (28) is formed; a rotor assembly (7) having a rotor (70) and the shaft (72) rotating integrally with the rotor (70); a stator (50) giving torque to the rotor (70) provided in an outer part of the casing (3); and a gear coupling body having an inner gear (60) for discharging the fluid and an outer gear (61) engaged with the inner gear (60). To transmit torque from the shaft (72) to the inner gear (60), a shaft end part member (81) is coupled with the shaft (72). The outer shape of the shaft end part member (81) has a pair of engagement faces for being engaged with an inside diameter part of the inner gear (60) and an automatic aligning face curved in an axial direction of the rotational shaft (72) of the rotor assembly (7). The inner gear (60) and the outer gear (61) are automatically positionally adjusted inside a gear chamber. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a flat plate pump that can be used not only for a spacecraft thermal control system but also for cooling medical devices and electronic devices.

A space control system such as an artificial satellite or a space station uses a heat control system to cool heat generated from an onboard electronic device. It is necessary to use a mechanical pump as a mechanical fluid drive source in a thermal control system of a spacecraft that generates a large amount of heat. A drive mechanism such as a mechanical pump uses a device that supports a movable member such as a rolling bearing device, a ball screw device, and a linear guide device so as to be displaceable.
In addition, equipment used in outer space, particularly equipment used in artificial satellites and space stations, is difficult to replace parts and requires high durability. The measures for supporting the movable member used in such a device are desired to be simple in order to reduce failure, and a structure that does not require a lubricant is desired.

  As a conventional mechanical space pump device serving as a refrigerant driving source, a trochoid gear pump using a cylindrical radial type motor (a stator encloses a rotor) described in Patent Document 1 is known. . The pump includes a housing, a shaft provided in the housing, a sliding bearing member that rotatably supports the shaft, a driving unit having a rotor and a stator, and a gear combination that is connected to the shaft and discharges fluid. Including. In this pump, the shaft is driven by the driving means, and the fluid sucked from the suction port can be discharged from the discharge port by flowing down the flow path.

However, this conventional pump using a radial type motor has an axially arranged gear combination including an outer gear and an inner gear and a rotor of driving means inside a cylindrical cylindrical member, and surrounds the rotor. A stator is provided.
Then, the fluid is sucked from one end of the housing, and the fluid is discharged from the other end. For this reason, a length is required in the axial direction of the cylindrical shape, and there is a drawback that it cannot be sufficiently downsized and flattened.

In addition, a trochoid gear pump using an axial type motor (rotor and stator are installed in parallel in the axial direction) has a pressure-resistant property so that a partition wall between the inner gear, outer gear and rotor (functions as a casing). There is a problem that it is difficult to flatten the plate.
A pump device used in a spacecraft is desired to be small and light. In addition to the field of space development, there is a demand for a small, flat-type pump device not only in the field of space development, but also in the field of applications such as portable artificial dialyzers and artificial hearts in the medical field, and cooling devices for high heat generation electronic devices such as computers. is there.
There is also a need for a bearing mechanism that supports a shaft that has a simple structure and does not require a lubricant in the pump device.
In addition, there is a demand for a mechanism that smoothly transmits the rotational force from the shaft to the gear in the pump device.
There is also a need for a pump device that has a plurality of discharge ports and can stably supply fluid to a plurality of locations.

JP 2002-276658 A

The present invention has been made to solve such problems, and an object of the present invention is to provide a small, flat plate-type trochoid gear pump device that improves volumetric efficiency and pump efficiency. Is to provide a device.
Another object of the present invention is to provide a mechanism for smoothly transmitting a rotational force from a shaft to a gear in a pump device.

  Another object of the present invention is to provide a pump device having a plurality of discharge ports for one suction port. Another object of the present invention is to provide a pump device that is less susceptible to downstream influences and that can evenly distribute fluid to a plurality of discharge ports with a single pump device.

In one aspect of the present invention, the flat plate pump device comprises:
A flat casing having a rotor chamber and a gear chamber in which a fluid flow path communicating the suction port and the discharge port is formed;
A rotor assembly having a disk-like rotor disposed in the rotor chamber and a shaft that rotates integrally with the rotor;
A gear combined body having a flat plate type inner gear and a flat plate type outer gear meshing with the inner gear disposed in the gear chamber, and a disk-shaped stator provided on the outside of the casing and providing a rotational force to the rotor.
A shaft end member is coupled to the shaft to transmit rotational force from the shaft to the inner gear, and the outer shape of the shaft end member has a pair of engagement surfaces for engaging with an inner diameter portion of the inner gear. A self-aligning surface that curves in the axial direction of the rotating shaft of the rotor assembly, and the inner gear and the outer gear are automatically adjusted in position in the gear chamber.

The engagement surface of the shaft end member may be substantially flat.
The self-aligning surface of the shaft end member may have a spherical shape that curves in the axial direction of the rotation axis of the rotor assembly and in a direction perpendicular to the rotation axis.
The self-aligning surface of the shaft end member may be curved in the axial direction of the rotation axis of the rotor assembly, but may not be curved in a direction perpendicular to the rotation axis.

According to the present invention, in a small, thin, flat plate type pump device, the driving force can be appropriately transmitted to the inner gear by the engagement surface of the shaft end member coupled to the shaft. Since the contact area between the self-aligning surface of the shaft end member and the inner gear is small, the inner gear and the outer gear can rotate slightly in a plane parallel to the shaft in the gear chamber and can move up and down. it can. Therefore, the gear automatically moves to a position where it can rotate smoothly (automatic adjustment).
Thereby, the clearance gap between a gear and a casing can be made smaller than the conventional pump, and volume efficiency can be improved.

In the flat plate pump device, instead of forming the self-aligning surface on the shaft end member, it is also possible to form the self-aligning surface on the inner gear. Alternatively, self-aligning surfaces can be formed on both the shaft end member and the inner gear.
The engaging portion that receives the shaft end member of the inner gear has a pair of self-aligning surfaces that are curved in the axial direction of the inner gear, and the inner gear and the outer gear are automatically adjusted in position. May be.

  In another aspect, the present invention relates to a shaft end member coupled to the shaft for transmitting rotational force from the shaft to the inner gear. The shaft end member includes a casing having a fluid passage formed therein for communicating a suction port and a discharge port and having a rotor chamber and a gear chamber, a rotor disposed in the rotor chamber, and a shaft rotating integrally with the rotor A rotor assembly having an inner gear and an outer gear that meshes with the inner gear and a stator that is provided outside the casing and that provides a rotational force to the rotor.

The outer shape of the shaft end member has a pair of engagement surfaces for engaging with an inner diameter portion of the inner gear, and an automatic alignment surface curved in the axial direction of the rotation shaft of the rotor assembly, The inner gear and the outer gear are automatically adjusted in position.
Thereby, in a pump apparatus, a rotational force can be smoothly transmitted from a shaft to an inner gear, and the clearance gap between a gear and a gear chamber can be made smaller than the conventional pump apparatus.

In another aspect, the present invention relates to an inner gear capable of transmitting a rotational force from a shaft end member coupled to the shaft. The inner gear includes a casing having a rotor chamber and a gear chamber in which a fluid flow path communicating the suction port and the discharge port is formed, and a rotor having a rotor disposed in the rotor chamber and a shaft that rotates integrally with the rotor. The assembly is used in a pump apparatus including an assembly, a gear combination having an inner gear and an outer gear that meshes with the inner gear, and a stator that is provided outside the casing and that provides a rotational force to the rotor.
The engagement portion for receiving the shaft end member of the inner gear is a pair of engagement surfaces for engaging with the engagement surface of the shaft end member, and an automatic curve that curves in the axial direction of the rotation shaft of the inner gear. The inner gear and the outer gear are automatically adjusted in position.

A pump device according to another aspect of the present invention has a plurality of discharge ports. In another aspect of the present invention, the flat plate pump device comprises:
A flat casing having a fluid suction port, a plurality of discharge ports, and a rotor chamber and a gear chamber communicating with these ports;
A shaft having a rotation axis perpendicular to the direction of the surface of the casing;
A disc-shaped rotor disposed in the rotor chamber and rotating integrally with the shaft;
A gear combination having a flat plate inner gear arranged in the gear chamber and rotated by the shaft, and a flat plate outer gear meshing with the inner gear, and arranged along one surface of the casing, and a rotational force on the rotor A disk-shaped stator having a plurality of plate-shaped windings wound around the rotation axis of the rotor assembly and disposed around the rotation axis of the rotor.

  According to another aspect of the present invention, a pump device having a plurality of discharge ports can be obtained. Further, the fluid can be evenly distributed to the plurality of discharge ports.

  A suction passage in a direction perpendicular to the axis of the casing; and a plurality of discharge passages in a direction perpendicular to the axis of the casing; fluid is sucked from the suction port through the suction passage; It is preferable that fluid is discharged from the plurality of discharge ports through the plurality of discharge passages.

  The casing is disposed in close contact with one surface of the gear case in which the gear chamber for housing the inner gear and the outer gear is formed, and a discharge port and a discharge passage are formed to rotate the shaft. A bearing case that is freely supported, disposed in close contact with the other surface of the gear case, disposed in close contact with the upper lid on which the second discharge port and the second discharge passage are formed, and the bearing case; A motor case in which the rotor chamber that rotatably accommodates the rotor is formed, and the gear chamber of the gear case and the rotor chamber of the motor case include the fluid suction port, the first, It is preferable to communicate with the second discharge port.

According to the present invention, since the inner gear and the outer gear are automatically adjusted in the gear chamber, the gear rotates smoothly, and the gap between the gear and the gear chamber can be made smaller than that of the conventional pump device. Volumetric efficiency can be improved.
In the pump device, a mechanism for smoothly transmitting the rotational force from the shaft to the pump can be obtained.
Further, a pump device having two discharge ports can be obtained for one suction port. In addition, it is possible to obtain a pump device that is less susceptible to downstream influences and that can evenly distribute the fluid to the two discharge ports with a single pump device.
The pump device of the present invention is suitable for use in a spacecraft. Further, it is also suitable for use as a pump used for a medical device such as a portable artificial dialyzer or an artificial heart, or as a pump used for a cooling device of an electronic device having a large heat generation such as a computer.

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view showing a pump device 1 according to an embodiment of the present invention, and FIG. 2 is a top view of the pump device 1 with the upper cover of FIG. 1 removed. FIG. 3 is an exploded perspective view of the pump device 1. In FIG. 3, bolts, nuts, and O-rings are omitted.
The pump device 1 is a device for circulating a refrigerant. The pump device 1 is mounted on a spacecraft such as an artificial satellite and a space station, and is suitable for circulating a refrigerant in order to cool other on-board electronic devices. Moreover, it is suitable for using as a pump of fluid drive sources, such as a medical device and an electronic device cooling device.
In the present specification, “up” means the upward direction in FIG.

A pump device 1 according to an embodiment of the present invention includes a casing 3 in which a refrigerant flow path 2 is formed, a stator assembly 50 on the lower side of the casing 3, and a reinforcing plate 90. In the casing 3, the rotor assembly 7 and the gear combined body 10 having the inner gear 60 and the outer gear 61 are provided. A motor is constituted by the rotor 70 of the rotor assembly 7 accommodated in the casing 3 and the stator assembly 50.
In the embodiment of the present invention, liquid ammonia is circulated as a refrigerant, but other fluids such as ethanol and water can be circulated.

The casing 3 includes an upper lid 11, a gear case 20, a bearing case 30, and a motor case 40.
A stator assembly 50 having a metal core 51, a wiring portion 52, and a winding 53 is overlaid on the lower side of the casing 3. A reinforcing plate 90 is overlaid on the lower side of the stator assembly 50. The upper lid 11, the gear case 20, the bearing case 30, the motor case 40, the stator assembly 50, and the reinforcing plate 90 are overlapped in this order.

The upper lid 11 and the gear case 20 are fixed to the screw holes formed in the bearing case 30 with bolts. The bearing case 30, the motor case 40, the stator assembly 50, and the reinforcing plate 90 are fixed by bolts and nuts through a plurality of through holes provided in the respective parts.
Alternatively, the whole can be fixed by bolts and nuts penetrating from the upper lid 11 to the reinforcing plate 90.

  Hereinafter, the components constituting the casing 3, the stator assembly 50 thereunder, and the reinforcing plate 90 will be described with reference to the drawings. 4 is a top view of the upper lid 11, and FIG. 5 is a sectional view taken along line 5-5 of FIG. The upper lid 11 has a disk shape, and its axis coincides with the axis of the casing 3. A plurality (six locations in the illustrated example) of through-holes 13 penetrate from the upper surface 14 to the lower surface 15 in the outer peripheral portion. A portion near the upper surface of the through-hole 13 is formed with a large-diameter portion 16, which can receive a bolt head or nut.

  6 is a top view of the gear case 20, and FIG. 7 is a cross-sectional view taken along line 7-7 of FIG. A gear case 20 is superimposed on the lower side of the upper lid 11. The axis of the gear case 20 coincides with the axis L3 of the casing 3. The gear case 20 has a disk shape as a whole, and a gear chamber 22 is formed at the center. In the outer periphery of the gear case 20, a plurality of (six in the illustrated example) through holes 23 for passing bolts penetrate from the upper surface 24 to the lower surface 25. A gear chamber 22 having a cylindrical inner peripheral surface is formed at the center. The axis L22 of the gear chamber 22 is formed so as to be offset from the axis L21 of the gear case 20. As will be described later, the outer gear 61 and the inner gear 60 are accommodated in the gear chamber 22.

  An annular groove 26 is formed on the upper surface 24 of the gear case 20 so as to surround the gear chamber 22, and an O-ring 29 is accommodated therein so that airtightness can be secured between the lower surface 15 of the upper lid 11. It has become. An annular groove 27 is formed on the lower surface 25 of the gear case 20 so as to surround the gear chamber 22, and an O-ring 45 is accommodated therein to ensure airtightness with the upper surface of the bearing case 30 described later. Be able to. The O-ring is made of silicon or fluorine elastomer resin.

8 is a top view of the bearing case 30, and FIG. 9 is a cross-sectional view taken along line 9-9 of FIG. A bearing case 30 is superimposed on the lower side of the gear case 20. The axis of the bearing case 30 coincides with the axis L3 of the casing 3. A through hole 33a through which the shaft 72 passes is formed at the center of the bearing case 30. The through hole 33a is formed with a bearing recess 33b having an enlarged inner diameter and a bearing retainer recess 33c having an enlarged inner diameter from the upper surface 31 toward the lower surface 32. An AC sliding bearing 5 is press-fitted and fitted into the bearing recess 33b. The axis of the slide bearing 5 coincides with the axis L3 of the casing 3. A bearing retainer is press-fitted and fitted into the bearing retainer recess 33c. The slide bearing 5 can also be bonded with a fluorine-based elastomer resin adhesive.
In the present embodiment, two parts of the sliding bearing 5 and the bearing retainer are used. However, the bearing retainer can be eliminated and only the sliding bearing 5 can be provided.

A gear chamber inlet port 37 extending in an arc shape in the circumferential direction is formed on the upper surface 31 of the bearing case 30 at a position shifted from the axis L30. The gear chamber inlet port 37 continues to the gear chamber 22. An inlet side pump passage 38 is connected to the lower side of the gear chamber inlet port 37, and the inlet side pump passage 38 penetrates to the lower surface 32 of the bearing case 30. In a state where the casing 3 is assembled, the inlet-side pump passage 38 is continuous with a rotor chamber 43 of a motor case 40 described later.
A gear chamber outlet port 34 extending in an arc shape in the circumferential direction is formed at a position opposite to the gear chamber inlet port 37 on the upper surface 31 of the bearing case 30. The gear chamber outlet port 34 continues from the gear chamber 22. Under the gear chamber outlet port 34, an outlet side pump passage 35 extends and extends in the axial direction of the bearing case 30. The outlet pump passage 35 is connected to a discharge passage 36 extending in the radial direction of the bearing case 30 at the lower end portion thereof. A discharge port 28 is formed at the tip of the discharge passage 36. A pipe is joined to the discharge port 28.

An annular groove 39 for accommodating the O-ring 49 is formed on the lower surface 32 of the bearing case 30.
In the outer peripheral portion of the bearing case 30, a plurality of (five places in the illustrated example) through holes for passing bolts penetrate from the upper surface to the lower surface. A plurality of screw holes (six locations in the illustrated example) are formed slightly inside the through hole. This screw hole is for screwing the upper lid 11 and the gear case 20 to the bearing case 30.

10 is a top view of the motor case 40, and FIG. 11 is a cross-sectional view taken along the line 11-11 in FIG. A motor case 40 is superimposed on the lower side of the bearing case 30. The axis of the motor case 40 coincides with the axis L3 of the casing 3. A rotor chamber 43 for accommodating the rotor 7 is formed at the center of the upper surface 41 of the motor case 40. A bearing recess 44 for receiving a bearing is formed at the center of the rotor chamber 43, and the sliding bearing 6 is fitted therein. The central lower surface 42b of the motor case 40 (below the bearing recess 44) is flush with the outer peripheral lower surface 42a of the motor case 40. Therefore, in a state where the pump device 1 is assembled, the lower surface 42b of the central portion of the motor case 40 is in contact with the upper surface of the metal core 51 of the stator assembly 50, and the lower surface of the metal core 51 is in contact with the upper surface of the reinforcing plate 90. Therefore, even if the thickness of the central portion lower surface 42b is thin, it is supported by the reinforcing plate 90, so that a high pressure resistance can be obtained.
The flow path 2 is connected from the rotor chamber 43 of the motor case 40 to the inlet pump passage 38 and the gear chamber inlet port 37 of the bearing case 30.

  A suction passage 46 is formed in the radial direction from one end of the rotor chamber 43. A suction port 48 is formed at the tip of the suction passage 46, and the suction port 48 is welded to the pipe. An annular groove 47 for accommodating an O-ring 49 is formed on the upper surface 41 of the motor case 40. An O-ring 49 is accommodated between the annular groove 39 of the bearing case 30 and the annular groove 47 of the motor case 40, and airtightness can be secured between the bearing case 30 and the motor case 40. An annular stator chamber 57 is formed around the bearing recess 44 on the lower surface 42 of the motor case 40. The wall pressure between the rotor chamber 43 and the stator chamber 57 is relatively thin. A winding 53 is accommodated in the stator chamber 57. At least a portion between the rotor chamber 43 and the stator chamber 57 of the motor case 40 needs to be made of a magnetically permeable material in order to transmit the magnetic lines of force from the winding 53 to the rotor 70.

The upper lid 11, the gear case 20, the bearing case 30, and the motor case 40 constitute the casing 3. In this state, the axis of the upper lid 11, the axis of the gear case 20, the axis of the bearing case 30, and the axis of the motor case 40 coincide with the axis L3 of the casing 3.
In the casing 3, a flow path 2 that connects the suction port 48 and the discharge port 28 is formed. The flow path 2 includes at least a suction passage 46, a rotor chamber 43, an inlet pump passage 38, a gear chamber inlet port 37, a gear chamber 22, a gear chamber outlet port 34, an outlet pump passage 35, and a discharge passage 36 in this order. ing.

12 is a top view of the stator assembly 50, and FIG. 13 is a cross-sectional view taken along line 13-13 of FIG. A stator assembly 50 is overlaid on the lower side of the motor case 40 constituting the casing 3. The axis L5 of the stator assembly 50 coincides with the axis L1 of the upper lid 11. The stator assembly 50 includes a disk-shaped metal core 51, a wiring portion 52 provided in a disk shape on the upper surface thereof, and a winding 53 thereon. The wiring part 52 and the winding 53 (armature coil) constitute a stator. A conductive wire is taken out from the wiring portion 52 in one direction. In the illustrated example, six windings 53 are provided adjacent to each other at equal intervals on the same circumference centered on the axis L3. Each of the windings 53 is wound a plurality of times in a substantially three-drawn shape in a direction parallel to the surface of the metal core 51 as shown in the figure. Both ends of each of the windings 53 are drawn out and connected to the wiring part 52, and current can flow from a power supply part (not shown).
In the assembled state of the pump device 1, the winding 53 of the stator assembly 50 is accommodated in the stator chamber 57 formed on the lower surface 42 of the motor case 40 and surrounded by the six windings 53 of the stator assembly 50. The lower surface 42b of the central part of the motor case 40 is inserted into the central recess.

A rotational force can be applied to the rotor 70 by passing a current through the windings 53 of the stator assembly 50 in order.
The number of windings 53 provided in the stator assembly 50 may be plural, and is not limited to six.

14 is a bottom view of the reinforcing plate 90, and FIG. 15 is a cross-sectional view taken along line 15-15 of FIG. The reinforcing plate 90 has a disk shape, and its axis coincides with the axis of the casing 3. A plurality of (five places in the illustrated example) through-holes 93 penetrate from the upper surface 91 to the lower surface 92 in the outer peripheral portion. A portion near the lower surface 92 of the through-hole 93 is formed with a large-diameter portion 94 that can receive a bolt head or nut. The reinforcing plate 90 can withstand high pressure applied in the casing 3.
These members can be fixed with nuts through bolts through the outer peripheral portions of the bearing case 30, the motor case 40, the stator assembly 50, and the reinforcing plate 90.

  Next, the rotor assembly 7 accommodated in the casing 3 will be described. 16 is a cross-sectional view of the rotor assembly 7 (a state where the shaft end member 81 is disassembled), and FIG. 17 is a bottom view. The rotor assembly 7 includes a rotor 70, and the rotor 70 includes a rotor substrate 74 and a magnet 78. The rotor 70 is accommodated in the rotor chamber 43 in the assembled state. The rotor assembly 7 further includes a shaft 72 and a shaft end member 81. The rotor substrate 74 is disc-shaped and has a hole 75 for receiving the shaft 72 in the center. The shaft 72 passes through the hole 75 of the rotor substrate 74 and extends downward. The rotor substrate 74 hangs down from the outer peripheral portion in the axial direction, and a magnet accommodating portion for accommodating a magnet is formed on the back surface of the rotor substrate 74.

The magnet 78 has a donut shape, and N poles and S poles are alternately formed in the circumferential direction. In the illustrated example, the number of N poles and S poles is four. The magnet 78 is fixed to the magnet housing portion on the lower surface of the rotor substrate 74 with an adhesive or the like.
The number of N poles and S poles is not limited to four, but may be plural.

  18 is a front view of the shaft 72, and FIG. 19 is a right side view. The shaft 72 is made of stainless steel and has a cylindrical shape. Since one end portion 77 in the axial direction of the shaft 72 is fitted with the shaft end member 81, a part of the circumferential direction has a planar shape. An AC shaft lower end 76 is embedded in the other end of the shaft 72.

20 is a perspective view of the shaft end member 81, FIG. 21 is a top view, and FIG. 22 is a cross-sectional view taken along the line 22-22 in FIG. 20-23, let the axial direction of the shaft 72 be az direction, and two directions perpendicular | vertical to this shall be an x direction and a y direction.
A shaft end member 81 is fixed to one end 77 of the shaft 72. The shaft end member 81 is provided with an engaging hole 82 that is partially flat for receiving the one end 77 of the shaft 72 at the center, and the one end 77 of the shaft 72 is fitted into the engaging hole 82. Fixed.

The outer peripheral portion of the shaft end member 81 has two engaging surfaces 83 parallel to the y axis. The engaging surface 83 is a surface for engaging with the engaging portion of the inner gear 60 to transmit the rotational force to the inner gear 60, and is substantially flat in this embodiment.
In the conventional shaft end member 81, the outer peripheral portion other than the two engaging surfaces 83 of the shaft end member 81 has two surfaces that are straight in the z-axis direction and curved in the x-axis direction, which will be described later. It is adapted to fit with the inner gear engaging portion (FIG. 40).
In the first embodiment of the present invention, the outer peripheral portion of the shaft end member 81 other than the two engaging surfaces 83 is a self-aligning surface 84 having curvatures in the z-axis direction and the x-axis direction. FIG. 20 shows a shape having a self-aligning surface 84.

  In the first embodiment, since the self-aligning surface 84 is a curved surface, the contact area between the outer peripheral portion of the self-aligning surface 84 of the shaft end member 81 and the engaging portion of the inner gear 60 is small. The inner gear 60 can rotate slightly in the gear chamber 22 and can move up and down. Therefore, the inner gear 60 and the outer gear 61 are automatically moved to a position where they can smoothly rotate within the gear chamber 22, that is, are automatically aligned. The self-aligning surface 84 is a surface for automatically adjusting the position of the gear. Therefore, even if there is a dimensional error or an attachment position error, the gear can rotate smoothly. The gap between the gear chamber and the gear can be made smaller than before, and as a result, the leakage (back flow) of the pump is reduced and the volumetric efficiency is increased.

  FIG. 23 is a perspective view of a shaft end member 81 ′ according to the second embodiment. The outer peripheral portion of the shaft end member 81 ′ has two engaging surfaces 83 parallel to the y-axis. The engagement surface 83 is a surface for transmitting a rotational force to the inner gear 60. Further, it has two self-aligning surfaces 85 that are straight in the x-axis direction and curved in the y-direction. Other parts are the same as those of the shaft end member 81 according to the first embodiment. Since the contact area between the self-aligning surface 85 of the shaft end member 81 ′ and the engaging portion of the inner gear 60 according to the second embodiment is small, the inner gear 60 and the outer gear 61 are the same as in the first embodiment. Is automatically adjusted.

In the first and second embodiments, the two engagement surfaces 83 of the shaft end member 81 are flat surfaces. However, the engaging surface is not limited to a flat surface as long as the rotational force can be transmitted to the inner gear 60, and may be a surface having a curvature.
In this way, the rotor substrate 74, the magnet 78, the shaft 72, and the shaft end member 81 are combined to constitute the rotor assembly 7.

  When assembling the rotor assembly 7, with the rotor substrate 74, the magnet 78, and the shaft 72 coupled, the shaft 72 is inserted from below the sliding bearing member 5 fitted in the bearing case 30, and A shaft end member 81 is fixed to one end 77 of the shaft 72 that has come out.

  In a state where the pump device 1 is assembled, the shaft 72 of the rotor assembly 7 is rotatably supported by the sliding bearing members 5 and 6 which are supporting members. 24 is a side view of the sliding bearing member 5, and FIG. 25 is a sectional view. In the present embodiment, the shaft 72 is supported at the center by the sliding bearing member 5 fitted in the bearing case 30. The plain bearing member 5 is made of AC and is formed in a short cylindrical shape. The axis of the sliding bearing member 5 is positioned as the axis L3 of the casing 3 in the assembled state. The sliding bearing member 5 is a radial bearing that supports the shaft 72 in the radial direction.

The shaft 72 is supported by the sliding bearing member 6 fitted in the bearing recess 44 of the motor case 40 at the lower end. The plain bearing member 6 is made of AC and has a short cylindrical shape. The sliding bearing member 6 is a radial / thrust composite bearing that supports the shaft 72 in the axial direction and the radial direction.
In the present embodiment, the plain bearing member 6 is an AC annular member, and is supported by an AC shaft lower end 76 embedded in the shaft 72 in the axial direction. However, the AC sliding bearing member 6 can be provided in both the radial direction and the axial direction, and the AC shaft lower end 76 embedded in the shaft 72 can be eliminated.
Thus, the shaft 72 is rotatably supported around the axis L4 from the radial direction and the axial direction in a state where the axis L4 coincides with the axis L3 of the casing 3.

  The radial gap between the shaft 72 and the sliding bearing members 5 and 6 is formed to have a dimension that allows the refrigerant in the rotor chamber 43 to enter the gap by capillary action. Thus, the gap is formed to be extremely small, and the shaft 72 can be stably supported.

The inner gear 60 is engaged with the outer side of the shaft end member 81, and the outer gear 61 is engaged with the outer side of the inner gear 60. The gear assembly 10 is configured by the inner gear 60 and the outer gear 61.
26 is a top view of the inner gear 60, and FIG. 27 is a cross-sectional view taken along line 27-27 of FIG. The inner gear 60 is formed with an engaging portion at the center for receiving the shaft end member 81. Part of the engaging portion is a flat surface 64 and the other portion is a circumferential surface 65. When the flat surface 64 of the inner gear 60 is engaged with the flat surface portion of the shaft end member 81, the inner gear 60 rotates when the shaft end member 81 rotates. The inner gear 60 has a plurality of teeth 62 (for example, four) formed on the outer periphery.

  28 is a top view of an inner gear 60 ′, which is another embodiment of the inner gear, FIG. 29 is a sectional view taken along line 29-29 in FIG. 28, and FIG. 30 is a sectional view taken along line 30-30 in FIG. It is. The inner gear 60 ′ has an automatic adjustment function. The engaging portion of the inner gear 60 ′ has a curved surface 66 in which a part is a flat surface 64 and the other part is curved in the axial direction. Since the contact area between the outer peripheral surface of the shaft end member 81 and the curved surface 66 of the engaging portion of the inner gear 60 'is small, as in the second and third embodiments of the shaft end member, The outer gear 61 can be automatically adjusted. When the inner gear 60 ′ of another embodiment is used, even when the outer peripheral surface of the shaft end member 81 is not curved in the axial direction, the contact between the outer peripheral surface of the shaft end member 81 and the engaging portion of the inner gear 60 ′. The area becomes smaller. Therefore, the inner gear 60 ′ and the outer gear 61 can be automatically adjusted.

31 is a top view of the outer gear 61, and FIG. 32 is a cross-sectional view taken along the line 32-32 of FIG. The outer gear 61 has a substantially cylindrical shape, and teeth 63 are formed on the inner periphery. The number of teeth 63 of the outer gear 61 is one more than the number of teeth 62 of the inner gear 60. As shown in FIGS. 1 and 2, the outer gear 61 is disposed outside the inner gear 60.
The inner gear 60 and the outer gear 61 are made of AC.

  FIG. 33 is an exploded perspective view of the inner gear 60, the outer gear 61, and the rotor assembly 7. As shown in FIG. 33, a substantially spherical shaft end member 81 is press-fitted and fixed to one end 77 of the shaft 72. This shaft end member 81 is disposed inside the inner gear 60. Therefore, the inner gear 60 has its axis L60 coincident with the axis L21 (L3) of the gear case 20. The outer gear 61 is disposed outside the inner gear 60 in a state of meshing with the inner gear 60. The outer gear 61 has an outer diameter slightly smaller than the inner peripheral surface of the gear chamber 22, and its axis L 61 is aligned with the axis L 22 of the gear chamber 22, and is eccentric from the inner gear 60.

  The inner gear 60, the outer gear 61, and the portion surrounding the gear chamber 22 form a positive displacement pump, specifically, a trochoid gear pump. In this pump device, a plurality of pressure chambers are formed between the inner gear 60 and the outer gear 61, and when the inner gear 60 is rotated by the rotation of the shaft 72, the outer gear 61 rotates along with this and feeds liquid.

  The rotor 70 and the stator assembly 50 form a motor as drive means. By sequentially energizing the windings 53 of the stator assembly 50, a rotational force is applied to the rotor 70 by a magnetic action with the magnet 78 of the rotor 70. The shaft 72 coupled to the rotor 70 is rotationally driven, and the inner gear 60 is rotated by the shaft end member 81 at the tip of the shaft 72, the outer gear 61 is rotated, the pump device is driven, and the refrigerant is supplied from the suction port 48. Inhalation can flow down the flow path 2 and discharge from the discharge port 28.

  34-37 show a pump apparatus 100 according to another aspect of the present invention. 34 is a cross-sectional view of the pump device 100, and FIG. 35 is an exploded perspective view. The pump device 100 has one suction port 48 and two discharge ports 28 and 128. A discharge passage 36 and a discharge port 28 are provided in the bearing case 30. In the pump device 100, a discharge passage 136 and a discharge port 128 are further provided in the upper lid 111.

36 is a bottom view of the upper lid 111 used in the pump device 100, and FIG. 37 is a cross-sectional view taken along line 37-37 of FIG. The upper lid 111 has a disk shape, and its axis coincides with the axis L 3 of the casing 103. A plurality of through holes 113 for passing bolts penetrate from the upper surface 114 to the lower surface 115 in the outer peripheral portion of the upper lid 111.
A gear chamber outlet port 134 extending in an arc shape in the circumferential direction is formed at a position shifted from the axis L3 of the lower surface 115 of the upper lid 111. An outlet pump passage 135 extending in the axial direction of the upper lid 111 is connected to the upper side of the gear chamber outlet port 134. The outlet pump passage 135 is connected to a discharge passage 136 extending in the radial direction of the upper lid 111. A second discharge port 128 is formed at the tip of the discharge passage 136. A pipe is joined to the second discharge port 128.

Other members of the casing 103 are the same as those of the casing 3. The other members other than the casing 103 of the pump device 100 are the same as the members of the pump device 1.
The casing 103 is formed with a flow path 2 that communicates the suction port 48, the discharge port 28, and the second discharge port 128. In the flow path 2, at least the suction passage 46, the rotor chamber 43, the inlet pump passage 38, the gear chamber inlet port 37, and the gear chamber 22 are connected in this order. Further, the flow path 2 branches in the gear chamber 22. One channel 2 is connected to the gear chamber outlet port 34, the outlet pump passage 35, the discharge passage 36, and the discharge port 28 in the same manner as the casing 3, and the other channel 2 ′ is connected to the gear chamber outlet port 134, The outlet side pump passage 135, the second discharge passage 136, and the second discharge port 128 are connected.

  The pump device 100 applies a rotational force to the rotor 70 by sequentially energizing the windings 53 of the stator assembly 50. The shaft 72 coupled to the rotor 70 is rotationally driven, the shaft end member 81 at the tip of the shaft 72 is rotated, the inner gear 60 is rotated, the outer gear 61 is rotated, the pump device is driven, and the fluid is supplied from the suction port 48. Inhalation can flow down the flow path 2, branch from the gear chamber into two flow paths 2, 2 ′, and discharge from the two discharge ports 28, 128.

In the pump device 100, the flow path branches from the gear chamber at two gear chamber outlet ports, and two discharge ports are provided for one suction port. Since the gear chamber outlet port is provided symmetrically above and below the gear, the amount of fluid discharged from the two discharge ports is approximately equal to about 1/2 of the amount of fluid to be sucked.
If the flow path is branched at the tip of the discharge port of the pump, there is a disadvantage that it is easy to be influenced downstream of the branch point and it is difficult to evenly distribute the fluid. Since the pump device 100 branches when the fluid exits the gear chamber, the pump device 100 is less susceptible to downstream effects and can distribute the fluid evenly.

  38 and 39 show performance test results of the pump device 1 according to the embodiment of the present invention. FIG. 38 is a graph showing the relationship between the rotational speed, the discharge amount, and the total pressure of the pump device 1 using ethanol at 20 ° C. FIG. 39 is a graph showing the relationship between the total pressure of the pump apparatus 1 using ethanol at 20 ° C., the discharge amount, the shaft power, the rotation speed, and the pump efficiency. According to the embodiment of the present invention, it is possible to obtain a pump device that is small and thin and has the same performance as a conventional trochoid gear pump.

  The slide bearing member is made of AC and can be supported so that the shaft can rotate smoothly. Since AC has high chemical resistance, it is not damaged even if it is arranged in the flow path. The gap between the shaft and the sliding bearing member is formed to be extremely small so as to further stabilize the rotation of the shaft.

  Liquid ammonia, which is a refrigerant, can enter the extremely small gap by capillary action. Further, the plain bearing made of AC can use the fluid as a good lubricant regardless of the type of fluid. Therefore, liquid ammonia, alcohol-based refrigerants, chemicals, water, etc. can be used. Accordingly, the pump device can interpose the fluid to be delivered as a lubricant, and achieve a smoother shaft rotation. Since the bearing can be configured by using a plain bearing member having a simple structure, failure is reduced and maintenance can be minimized.

  AC has a small coefficient of friction, can suppress generation of frictional heat due to rotation of the shaft, and can prevent thermal expansion of the shaft and the sliding bearing member. Moreover, even if frictional heat is generated, AC has a small coefficient of thermal expansion, so that the change in the dimension of the gap between the shaft and the sliding bearing member is small, and stable rotation can be maintained. Further, the degree of wear is small, and even when used over a long period of time, wear powder does not come out and the fluid is not contaminated, and the dimension of the gap does not change, and a smooth and stable rotation can be realized over a long period of time.

  Further, the shaft, the plain bearing member and the rotor can be cooled by the fluid, and the stable performance of the pump can be maintained. Furthermore, the lower surface of the rotor case is thin, and the stator on the lower side of the rotor chamber can be cooled.

  As an embodiment of the present invention, an example of a pump device used in a spacecraft cooling system has been described. However, the system and method of the present invention are not limited to these. As the fluid, not only liquid ammonia but also various fluids such as alcohol-based refrigerants, chemicals, and water can be used, and the fluid can be applied to various technologies for delivering the fluid. For example, it can be used as a pump for a medical device such as a portable artificial dialyzer or an artificial heart. Moreover, it can also be used as a pump for a cooling device or the like of electronic equipment that generates a large amount of heat, such as a computer.

The schematic sectional drawing of the pump apparatus by embodiment of this invention. The top view of the state which removed the upper cover of the pump apparatus of FIG. The disassembled perspective view of the pump apparatus of FIG. The top view of an upper cover. Sectional drawing of an upper cover. The top view of a gear case. Sectional drawing of a gear case. The top view of a bearing case. Sectional drawing of a bearing case. The top view of a motor case. Sectional drawing of a motor case. The top view of a stator assembly. Sectional drawing of a stator assembly. The bottom view of a reinforcement board. Sectional drawing of a reinforcement board. Sectional drawing of a rotor assembly. The bottom view of a rotor assembly. The front view of a shaft. The right view of a shaft. The perspective view of 1st Embodiment of a shaft end part member. The top view of a 1st embodiment of a shaft end member. FIG. 22 is a sectional view taken along line 22-22 in FIG. The perspective view of 2nd Embodiment of a shaft edge part member. The side view of a sliding bearing member. Sectional drawing of a sliding bearing member. The top view of an inner gear. Sectional drawing of an inner gear. The top view of another embodiment of inner gear 60 '. FIG. 29 is a sectional view taken along line 29-29 in FIG. 28; FIG. 30 is a sectional view taken along line 30-30 in FIG. 28; The top view of an outer gear. Sectional drawing of an outer gear. The disassembled perspective view of a gear coupling body and a rotor assembly. Sectional drawing of the pump apparatus by another aspect. The disassembled perspective view of the pump apparatus by another aspect. The bottom view of the upper cover by another aspect. FIG. 37 is a sectional view taken along line 37-37 in FIG. 36; The graph which shows the rotation speed of a pump apparatus, discharge amount, and total pressure. The graph which shows the performance of a pump apparatus. The perspective view of the conventional shaft end part member.

Explanation of symbols

1 Pumping device
2 Flow path
3 Casing
5 Sliding bearing member
6 Sliding bearing member
7 Rotor assembly
10 Gear combination
11 Upper lid
20 Gear case
22 Gear room
28 Discharge port
29 O-ring
30 Bearing case
40 Motor case
43 Rotor chamber
44 Bearing recess
45 O-ring
48 Suction port
49 O-ring
50 Stator assembly
51 metal core
52 Wiring section
53 winding
57 Stator chamber
60 Inner Gear
61 Outer Gear
62 teeth
63 teeth
70 rotor
72 shaft
74 Board
78 Magnet
81 Shaft end member
90 Reinforcing plate
100 pumping equipment
111 Upper lid
128 Second discharge port

Claims (13)

A flat casing having a rotor chamber and a gear chamber in which a fluid flow path communicating the suction port and the discharge port is formed;
A rotor assembly having a disk-like rotor disposed in the rotor chamber and a shaft that rotates integrally with the rotor;
A flat plate pump device including a gear combined body having a flat plate type inner gear and a flat plate type outer gear that meshes with the inner gear disposed in the gear chamber, and a disk-shaped stator that is provided outside the casing and applies a rotational force to the rotor. And
A shaft end member is coupled to the shaft to transmit rotational force from the shaft to the inner gear, and the outer shape of the shaft end member has a pair of engagement surfaces for engaging with an inner diameter portion of the inner gear. And a self-aligning surface curved in the axial direction of the rotating shaft of the rotor assembly, and the position of the inner gear and the outer gear is automatically adjusted in the gear chamber.   The pump device according to claim 1, wherein the engagement surface of the shaft end member is substantially flat.   3. The pump device according to claim 2, wherein the self-aligning surface of the shaft end member has a spherical shape that is curved in an axial direction of a rotation axis of the rotor assembly and a direction perpendicular to the rotation axis.   3. The pump device according to claim 2, wherein the self-aligning surface of the shaft end member has a curved shape that is curved in the axial direction of the rotation axis of the rotor assembly but is not curved in a direction perpendicular to the rotation axis. . A flat casing having a rotor chamber and a gear chamber in which a fluid flow path communicating the suction port and the discharge port is formed;
A rotor assembly having a disk-like rotor disposed in the rotor chamber and a shaft that rotates integrally with the rotor;
A flat plate pump device including a gear combined body having a flat plate type inner gear and a flat plate type outer gear that meshes with the inner gear disposed in the gear chamber, and a disk-shaped stator that is provided outside the casing and applies a rotational force to the rotor. And
In order to transmit a rotational force from the shaft to the inner gear, a shaft end member is coupled to the shaft, and an engaging portion for receiving the shaft end member of the inner gear engages with an engaging surface of the shaft end member. And a self-aligning surface curved in the axial direction of the rotating shaft of the inner gear, and the inner gear and the outer gear are automatically adjusted in position in the gear chamber. A pump device characterized by. A casing having a rotor chamber and a gear chamber in which a fluid flow path communicating the suction port and the discharge port is formed, a rotor assembly having a rotor disposed in the rotor chamber and a shaft that rotates integrally with the rotor, Used in a pump unit including a gear coupling body having an inner gear and an outer gear that meshes with the inner gear and a stator that is provided outside the casing and that provides a rotational force to the rotor, and rotates from the shaft to the inner gear. A shaft end member coupled to the shaft for transmitting force,
The outer shape of the shaft end member has a pair of engagement surfaces for engaging with an inner diameter portion of the inner gear, and an automatic alignment surface curved in the axial direction of the rotation shaft of the rotor assembly, The inner gear and the outer gear are shaft end members that are automatically positioned within the gear chamber.   The shaft end member according to claim 7, wherein the engagement surface of the shaft end member is substantially flat.   The shaft end member according to claim 8, wherein the self-aligning surface of the shaft end member has a spherical shape that is curved in an axial direction of the rotation axis of the rotor assembly and a direction perpendicular to the rotation axis.   9. The shaft end according to claim 8, wherein the self-aligning surface of the shaft end member has a curved shape that is curved in an axial direction of a rotation axis of the rotor assembly but is not curved in a direction perpendicular to the rotation axis. Part member. A casing having a rotor chamber and a gear chamber in which a fluid flow path communicating the suction port and the discharge port is formed, a rotor assembly having a rotor disposed in the rotor chamber and a shaft that rotates integrally with the rotor, A shaft end coupled to the shaft, which is used in a pump assembly including a gear coupling body having an inner gear and an outer gear that meshes with the inner gear, and a stator that is provided outside the casing and that provides a rotational force to the rotor. An inner gear that can transmit the rotational force from the member,
The engagement portion for receiving the shaft end member of the inner gear is a pair of engagement surfaces for engaging with the engagement surface of the shaft end member, and an automatic curve that curves in the axial direction of the rotation shaft of the inner gear. An inner gear having an alignment surface, wherein the inner gear and the outer gear are automatically adjusted in position in the gear chamber. A flat casing having a fluid suction port, a plurality of discharge ports, and a rotor chamber and a gear chamber communicating with these ports;
A shaft having a rotation axis perpendicular to the direction of the surface of the casing;
A disc-shaped rotor disposed in the rotor chamber and rotating integrally with the shaft;
A gear combination having a flat plate inner gear arranged in the gear chamber and rotated by the shaft, and a flat plate outer gear meshing with the inner gear, and arranged along one surface of the casing, and a rotational force on the rotor A disk-shaped stator having a plurality of flat-plate windings wound around the rotation axis of the rotor assembly and arranged around the rotation axis of the rotor,
A flat plate pump device characterized by comprising:   A suction passage in a direction perpendicular to the axis of the casing; and a plurality of discharge passages in a direction perpendicular to the axis of the casing; fluid is sucked from the suction port through the suction passage; The pump device according to claim 11, wherein the fluid branches and discharges fluid from the plurality of discharge ports through the plurality of discharge passages. The casing is
A gear case in which the gear chamber for accommodating the inner gear and the outer gear is formed;
A bearing case that is disposed in close contact with one surface of the gear case, has a discharge port and a discharge passage, and rotatably supports the shaft;
An upper lid disposed in close contact with the other surface of the gear case and having a second discharge port and a second discharge passage;
A motor case which is disposed in close contact with the bearing case and forms the rotor chamber for rotatably accommodating the rotor;
The pump device according to claim 11, wherein the gear chamber of the gear case and the rotor chamber of the motor case are in communication with the fluid suction port and the first and second discharge ports. .

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