CN105370580A - Dynamic pressure bearing pump - Google Patents
Dynamic pressure bearing pump Download PDFInfo
- Publication number
- CN105370580A CN105370580A CN201510464508.1A CN201510464508A CN105370580A CN 105370580 A CN105370580 A CN 105370580A CN 201510464508 A CN201510464508 A CN 201510464508A CN 105370580 A CN105370580 A CN 105370580A
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- China
- Prior art keywords
- rotor
- dynamic pressure
- pressure groove
- hydraulic bearing
- groove
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/186—Shaftless rotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D11/00—Other rotary non-positive-displacement pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0606—Canned motor pumps
- F04D13/0633—Details of the bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/047—Bearings hydrostatic; hydrodynamic
- F04D29/0476—Bearings hydrostatic; hydrodynamic for axial pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D3/00—Axial-flow pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/001—Shear force pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
A pump a shaft portion arranged to extend in a vertical direction; a rotor portion arranged to surround an outer circumference of the shaft portion, and including a magnet; and a housing joined to the shaft portion, and arranged to contain the rotor portion. The housing includes a stator arranged opposite to the magnet; a rotor accommodating portion arranged to accommodate the rotor portion; and an inlet and an outlet each of which is arranged to pass through a portion of the rotor accommodating portion. A surface of at least one of the rotor portion, the shaft portion, and the rotor accommodating portion includes at least one first dynamic pressure groove arranged to support rotation of the rotor portion. A surface of at least one of the rotor portion and the rotor accommodating portion includes at least one second dynamic pressure groove arranged to transfer a fluid from the inlet to the outlet. The rotor portion includes a through hole arranged to pass therethrough in an axial direction.
Description
Technical field
The present invention relates to a kind of pump sent by fluid by the pressure effect of dynamic pressure groove.
Background technique
In recent years, the electronic component being built-in with CPU etc. is miniaturized component, and along with the increase of calculation process amount, the heating value of electronic component also becomes large.In order to cool these electronic components, having and refrigerant liquid is enclosed pipe, by the method making refrigerant liquid circulation carry out cooling electronic components.In order to cooling electronic components effectively, the Measures compare adopting pump that refrigerant liquid is circulated is effective.Further, along with the miniaturization of electronic component, the demand of the miniaturization of pump is had.
About existing miniature pump, such as, described in No. 2007-218154, Japanese Laid Open Patent.A kind of turbulence pump is disclosed in this publication, impeller, axle and drive unit is accommodated in its housing parts, wherein, described impeller is included in periphery and has the blade part in disc-shape of multiple blade and have the tubular bearing portion of bearing in inner circumferential; Impeller supports as moving vertically by described axle; Described drive unit is configured at around the bearing portion that impeller has, and vane rotary is driven.Housing parts has and holds the fluid delivery section of blade part and the drive unit accommodating part of containing drive device, and is formed with the position near the inner side of blade produces dynamic pressure dynamic pressure groove based on the rotation of impeller on the surface of the two sides of impeller or the housing parts relative respectively with the two sides of impeller.
In existing pump, impeller comprises and having for carrying multiple blade of fluid and having the tubular bearing portion of bearing in inner circumferential.In this pump, need to arrange the space holding blade part, therefore the more miniaturization of electronic component has difficulties.
Summary of the invention
A mode of execution according to the application, a kind of hydraulic bearing pump, described hydraulic bearing pump has: the axle portion extended along the vertical direction; Periphery, axle portion is surrounded, and there is the rotor part of magnet; And be connected with axle portion, and rotor part being contained in inner casing, casing has: the stator relative with magnet; Hold the rotor accommodating part of rotor part; And the inflow entrance of through rotor accommodating part and outflow opening, the surface at least one place in rotor part, axle portion and rotor accommodating part has the first dynamic pressure groove of supporting rotor portion rotation, the surface at least one place in rotor part and rotor accommodating part has the second dynamic pressure groove carried from inflow entrance to outflow opening by fluid, and rotor part has through hole through vertically.
A mode of execution according to the application, owing to being that the second dynamic pressure groove of the first dynamic pressure groove and the conveying fluid that can rotate is configured at rotor part by rotor part supporting, therefore not needing the space arranging blade part, can realize the miniaturization of pump.
The detailed description of the following preferred embodiment for the present invention, with reference to accompanying drawing, more clearly can understand above-mentioned and other feature of the present invention, key element, step, feature and advantage.
Accompanying drawing explanation
The longitudinal section of the pump of Fig. 1 involved by the first mode of execution.
The longitudinal section of the rotor part of Fig. 2 involved by the first mode of execution.
The plan view of the rotor part of Fig. 3 involved by the first mode of execution.
The worm's eye view of the rotor part of Fig. 4 involved by the first mode of execution.
The longitudinal section of the casing of Fig. 5 involved by the first mode of execution.
The longitudinal section of the casing of Fig. 6 involved by variation.
The longitudinal section of the casing of Fig. 7 involved by variation.
The longitudinal section of the pump of Fig. 8 involved by variation.
The longitudinal section of the pump of Fig. 9 involved by variation.
The longitudinal section of the pump of Figure 10 involved by variation.
The longitudinal section of the pump of Figure 11 involved by the second mode of execution.
The longitudinal section of the casing of Figure 12 involved by the second mode of execution.
The longitudinal section of the casing of Figure 13 involved by variation.
The longitudinal section of the casing of Figure 14 involved by variation.
The longitudinal section of the casing of Figure 15 involved by variation.
Embodiment
In the present invention, the direction parallel with the running shaft of rotor is called " axis ", the direction of the rotating shaft direct cross with rotor is called " radial direction ", be called along the circular arc direction centered by the running shaft of rotor " circumference ".But above-mentioned " parallel direction " also comprises almost parallel direction.Further, above-mentioned " orthogonal direction " also comprises roughly orthogonal direction.
The longitudinal section of the pump 1 of Fig. 1 involved by the first mode of execution of the present invention.This pump 1 is such as connected with the pipe with refrigerant liquid, and is equipped on the electronic equipment making CPU etc. produce heat, and described pump 1 is to make the refrigerant liquid of cooling electronic apparatus be used at pipe Inner eycle.But pump of the present invention also can be used to, with the purposes of object conveying fluid except cooling, also can use the fluid except refrigerant liquid.Further, pump of the present invention also can be used to the purposes of the haulage device such as household appliances, automobile, medical equipment etc.
As shown in Figure 1, at the pump 1 of present embodiment, there is casing 10, rotor part 20 and axle portion 30.
Casing 10 is and the housing for carrying the pipe of fluid to be connected.Casing 10 has the connection mouth for being connected with pipe.Manage and fluid sent into the inflow entrance 11 of pump and be connected from the outflow opening 12 of pump displacement fluids.Casing 10 has the stator 40 relative with magnet 50, holds inflow entrance 11 and the outflow opening 12 of the rotor accommodating part 13 of rotor part 20 and through rotor accommodating part 13.Rotor part 20 is configured at the rotor accommodating part 13 of the inner side being arranged on casing 10.The periphery in axle portion 30 surrounds and has magnet 50 by rotor part 20.Stator 40 is configured at relative position with magnet 50, and by powering to stator 40, and rotor part 20 is rotated.The material of casing 10 such as both can adopt the metals such as stainless steel, also can adopt the resins such as LCP.
Axle portion 30 is configured at the inner side of casing 10.Axle portion 30 configures in the mode of through rotor accommodating part 13.The two ends in preferred axle portion 30 contact with casing 10.Further, also can the end in only axle portion 30 contact with casing 10.The material in axle portion 30 such as adopts the metals such as stainless steel.And the surface in axle portion 30 is processed as surface roughness and the little state of cylindricity by grinding etc.
Stator 40 has stator iron core 41 and multiple coil 42.Stator iron core 41 such as adopts stacked steel plate.Stator iron core 41 is such as fixed on casing 10 by Bond.Stator iron core 41 has the multiple poles tooth radially extended from core-back towards radial direction.Coil 42 is made up of the wire being wound in pole tooth.Multiple coil 42 circumferentially arranges at substantially equal intervals around running shaft 2.
Inflow entrance 11 is through to rotor accommodating part 13.Further, outflow opening 12 is through to rotor accommodating part 13.That is, the inside of pump 1 is communicated with to outflow opening 12 from inflow entrance 11 via rotor accommodating part 13.
Rotor part 20 is in roughly cylindric, and rotor part 20 is axle centered by axle portion 30, and inserts vertically for axle portion 30.Further, rotor part 20 is configured at rotor accommodating part 13.That is, rotor part 20 is configured at rotor accommodating part 13 in the mode of the axle outer circumferential face 31 surrounding axle portion 30.Magnet 50 is configured near the rotor outer periphery face 21 of rotor part 20.Magnet 50 configures in the mode diametrically opposed with stator 40.That is, axle portion 30, magnet 50 and stator 40 configure in mode overlapping diametrically respectively.The material of rotor part 20 such as both can adopt the metals such as stainless steel, also can adopt the resins such as LCP.
The rotor part 20 of present embodiment is in roughly cylindric, and rotor part 20 is axle centered by axle portion 30, and inserts vertically for axle portion 30.Rotor part 20 has rotor outer periphery face 21, rotor inner peripheral surface 22, upper rotor surface 23 and rotor lower surface 24.Rotor outer periphery face 21 and rotor inner peripheral surface 22 are axle the barrel surface almost parallel with central shaft centered by running shaft 2.Further, upper rotor surface 23 and rotor lower surface 24 are the circular surface roughly orthogonal with axle portion 30.Rotor outer periphery face 21 is relative across gap with casing inner peripheral surface 131, and this casing inner peripheral surface 131 is the surface of the inner side of rotor accommodating part 13.Rotor inner peripheral surface 22 is relative across gap with axle outer circumferential face 31.Further, upper rotor surface 23 and rotor lower surface 24 are relative across gap with the internal surface 132 of rotor accommodating part 13 respectively.
Inflow entrance 11 and outflow opening 12 are with through in the mode of internal surface 132 opening respectively.But the position of opening is not limited to this, also can any one in inflow entrance 11 and outflow opening 12 at casing inner peripheral surface 131 opening.
The surface at least one place in rotor part 20, axle portion 30 and rotor accommodating part 13 has the first dynamic pressure groove 60 of supporting rotor portion 20 rotation.More particularly, the surface at least one place in rotor inner peripheral surface 22 and axle outer circumferential face 31 has the radial dynamic pressure groove 61 as the first dynamic pressure groove 60.Further, the surface at least one place in the internal surface in rotor accommodating part 13, upper rotor surface 23 and rotor lower surface 24 has the axial hydrodynamic groove as the first dynamic pressure groove 60.More particularly, at upper rotor surface 23 with the surface at least one place of upper rotor surface 23 in the internal surface 132 that gap is relative, there is the upper axial hydrodynamic groove 62 as the first dynamic pressure groove 60.Further, at rotor lower surface 24 with the surface at least one place of rotor lower surface 24 in the internal surface 132 that gap is relative, there is the lower axial dynamic pressure groove 63 as the first dynamic pressure groove 60.
In the present embodiment, at rotor inner peripheral surface 22, there is radial dynamic pressure groove 61.But the position of radial dynamic pressure groove 61 is not limited to this, also can at rotor inner peripheral surface 22 and this two place of axle outer circumferential face 31 configuration radial dynamic pressure groove 61.
In the present embodiment, axial hydrodynamic groove 62 and lower axial dynamic pressure groove 63 on rotor part 20 has.Also any one in axial hydrodynamic groove 62 and lower axial dynamic pressure groove 63 can only be configured.Further, upper axial hydrodynamic groove 62 also can configure at upper rotor surface 23 and with upper rotor surface 23 across this two place of internal surface 132 that gap is relative.Further, lower axial dynamic pressure groove 63 also can configure at rotor lower surface 24 and with upper rotor surface 24 across this two place of internal surface 132 that gap is relative.
The surface at least one place in rotor part 20 and rotor accommodating part 13 has the second dynamic pressure groove 70 carried from inflow entrance 11 to outflow opening 12 by fluid.More particularly, the surface at least one place in rotor outer periphery face 21 and casing inner peripheral surface 131 has the second dynamic pressure groove 70.Further, the second dynamic pressure groove 70 also can in rotor outer periphery face 21 and the configuration of this two place of casing inner peripheral surface 131.
Rotor part 20 has through hole 80 through vertically.Further, the surface opening at least one place of through hole 80 in upper rotor surface 23 and rotor lower surface 24.In the present embodiment, through hole 80 is respectively at upper rotor surface 23 and rotor lower surface 24 opening.Further, preferred through hole 80 axle centered by running shaft 2, and configure abreast with central shaft.Further, through hole 80 also can be along inclined direction through relative to central shaft.More preferably through hole 80 is positioned at and leans on towards the position of the inner side of central shaft than the position of the inflow entrance 11 and outflow opening 12 that are arranged at rotor accommodating part 13.
Fluid is dispersed throughout the space of inflow entrance 11, rotor accommodating part 13 and outflow opening 12.When coil 42 to stator 40 provides driving current, produce magnetic flux at multiple poles tooth of stator iron core 41.Then, by the flux interaction between stator 40 and magnet 50, produce circumferential torque.Consequently, rotor part 20 axle centered by running shaft 2 rotates.By the rotation of rotor part 20, produce at the second dynamic pressure groove 70 and pump effect, thus fluid can be carried from inflow entrance 11 to outflow opening 12.Further, because rotor accommodating part 13 is full of by fluid, so produce kinetic pressure by the first dynamic pressure groove 60 between rotor part 20 and axle portion 30 and rotor accommodating part 13.By the rotation in this kinetic pressure supporting rotor portion 20.Rotor part 20 passes through the dynamic pressure effect of the first dynamic pressure groove 60 and the second dynamic pressure groove 70, rotates in a non-contact manner in rotor accommodating part 13.Thus, rotor part 20 does not rotate contiguously with axle portion 30 and casing 10, can provide rotor part 20, axle portion 30 and casing 10 do not produce wearing and tearing, the pump of long-life.Further, by non-contact, fluid can not be made to produce and to go bad, and carry out the conveying of fluid.Further, axle outer circumferential face 31 is narrower with the width in the gap in rotor outer periphery face 21 than casing inner peripheral surface 131 with the width in the gap of rotor inner peripheral surface 22.Because axle outer circumferential face 31 is narrower with the width in the gap in rotor outer periphery face 21 than casing inner peripheral surface 131 with the width in the gap of rotor inner peripheral surface 22, therefore rocking of rotor part 20 diminishes, and improves the running accuracy of rotor part 20.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
Through hole 80 configures in the mode connecting inflow entrance 11 side and outflow opening 12 side.At this moment, the hydrodynamic pressure of inflow entrance 11 side and outflow opening 12 side can become approximate equality.When producing bubble in fluid or flow into bubble, bubble is externally discharged from outflow opening 12.Therefore, it is possible to prevent bubble residence inner in pump.
Fig. 2 is the longitudinal section of rotor part 20.Rotor part 20 is the roughly cylindric of axle centered by axle portion 30.Rotor part 20 has rotor outer periphery face 21, rotor inner peripheral surface 22, upper rotor surface 23 and rotor lower surface 24.Rotor outer periphery face 21 and rotor inner peripheral surface 22 are axle and be almost parallel barrel surface relative to central shaft centered by running shaft 2.In addition, upper rotor surface 22 and rotor lower surface are the face of the toroidal roughly orthogonal with axle portion 30.
It is the radial dynamic pressure groove 61 of the first dynamic pressure groove 60 that rotor inner peripheral surface 22 has.Multiple man type chutes of the radial dynamic pressure groove 61 of present embodiment circumferentially arrange.Further, rotor inner peripheral surface 22 has two groups of dynamic pressure groove groups.These two groups of dynamic pressure groove groups are configured vertically side by side.Multiple man type chute has reflex part 611.Further, multiple man type chute has the outside dynamic pressure groove 612 and inner side dynamic pressure groove 613 that extend from reflex part 611.Outside dynamic pressure groove 612 is the dynamic pressure groove extended to upper rotor surface 23 or rotor lower surface 24 from reflex part 611.Further, inner side dynamic pressure groove 613 is the dynamic pressure groove extended along the center of rotor part 20 from reflex part 611.Multiple man type chute is configured to the fluid when axle rotates rotor part 20 centered by running shaft 2 and collects to reflex part 611.By coming together in the kinetic pressure of the fluid of reflex part 611, reducing rocking of rotor part 20, improving the running accuracy of rotor part 20.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
In the present embodiment, outside dynamic pressure groove 612 is identical length with inner side dynamic pressure groove 613.Further, also can a dynamic pressure flute length than another in two dynamic pressure grooves.More preferably outside dynamic pressure groove 612 is longer than inner side dynamic pressure groove 613.Because outside dynamic pressure groove 612 is long, because this increasing the kinetic pressure of rotor inner peripheral surface 22, improve the running accuracy of rotor part 20.
Rotor part 20 has through hole 80 between rotor outer periphery face 21 and rotor inner peripheral surface 22.Through hole 80 has opening portion respectively at upper rotor surface 23 and rotor lower surface 24.In the present embodiment, through hole 80 using running shaft 2 as central shaft, and configures substantially in parallel relative to central shaft.But be not limited to this, through hole 80 also along inclined direction can configure relative to central shaft.
Fig. 3 is the plan view of rotor part 20.Fig. 4 is the worm's eye view of rotor part 20.In figure 3, upper rotor surface 23 has the upper shed portion 81 of the opening as through hole 80.And in the diagram, rotor lower surface 24 has the under shed portion 82 of the opening as through hole 80.
In figure 3, upper rotor surface 23 has the upper axial hydrodynamic groove 62 as the first dynamic pressure groove 60.Upper axial hydrodynamic groove 62 is the multiple spiral chutes circumferentially arranged.Multiple spiral chute is configured at upper rotor surface 23 in rotor part 20 mode that during axle rotation, fluid collects from rotor outer periphery face 21 to the direction of rotor inner peripheral surface 22 centered by running shaft 2.By by the kinetic pressure of fluid collected, reduce rocking of rotor part 20, improve the running accuracy of rotor part 20.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
In the diagram, rotor lower surface 24 has the lower axial dynamic pressure groove 63 as the first dynamic pressure groove 60.Lower axial dynamic pressure groove 63 is the multiple spiral chutes circumferentially arranged, and lower axial dynamic pressure groove 63 has two groups of dynamic pressure groove groups.These two groups of dynamic pressure groove groups are respectively towards different direction.Wherein one group of dynamic pressure groove group be when centered by running shaft 2, axle rotates rotor part 20, internal circle groove 631 that fluid is collected from from rotor outer periphery face 21 to the direction of rotor inner peripheral surface 22.Another group dynamic pressure groove group be when centered by running shaft 2, axle rotates rotor part 20, by fluid from rotor inner peripheral surface 22 circumferential groove 632 to the conveying of the direction in rotor outer periphery face 21.Utilize the kinetic pressure of the fluid collected by internal circle groove 631, reduce rocking of rotor part 20, improve the running accuracy of rotor part 20.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.Further, the fluid transported by circumferential groove 632 is carried by rotor outer periphery face 21, can improve the discharge pressure of pump.
In the present embodiment, the under shed portion 82 of through hole 80 is configured between internal circle groove 631 and circumferential groove 632.More preferably, the part under shed portion 82 is overlapping with internal circle groove 631.At the internal configurations fluid of through hole 80.That is, in the inner side of rotor accommodating part, the fluid being configured at radial dynamic pressure groove 61, upper axial hydrodynamic groove 62, lower axial dynamic pressure groove 63 and through hole 80 is continuous print.When rotor part 20 centered by running shaft 2 axle rotate time, in the inner side of rotor accommodating part, fluid can radial dynamic pressure groove 61, on axial hydrodynamic groove 62, lower axial dynamic pressure groove 63 and through hole 80 path in circulate.Circulated in this path by fluid, reduce rocking of rotor part 20, improve the running accuracy of rotor part 20.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.Further, as mentioned above, through hole 80, owing to being positioned at the position in the inner part, position than the inflow entrance and outflow opening of being located at rotor accommodating part, therefore, does not hinder the fluid carried from inflow entrance to outflow opening.
The direction in upper shed portion 81 and under shed portion 82 is not limited at the loop direction of the fluid of through hole 80.Fluid also can flow under shed portion 82 from upper shed portion 81, and, also can be contrary with it.
Further, in the present embodiment, through hole 80 is constant from the aperture in 81 under shed portion of upper shed portion 82.But aperture is not limited to this, also can the aperture of opening portion of side less than the aperture of the opening portion of opposite side.
In the present embodiment, as shown in Figure 1, two groups of dynamic pressure groove groups that lower axial dynamic pressure groove 63 bearing of trend with dynamic pressure groove is different.That is, there is the shape of the dynamic pressure groove group of Fig. 4.Further, upper axial hydrodynamic groove 62 has the dynamic pressure groove group arranged in one direction.That is, there is the shape of the dynamic pressure groove group of Fig. 3.By the internal circle groove 631 and circumferential groove 632 that are configured at lower axial dynamic pressure groove 63, the fluid transported from inflow entrance 11 is separated respectively to the direction in rotor outer periphery face 21 and the direction of rotor inner peripheral surface 22.Discharged from outflow opening 12 via the second dynamic pressure groove 70 by the fluid that the direction to rotor outer periphery face 21 is carried.Further, the fluid carried by the direction to rotor inner peripheral surface 22 is by the rotation in the first dynamic pressure groove 60 supporting rotor portion 20.
Therefore, rotor part 20 by by a kind of fluid bearing of carrying to rotor accommodating part 13 from inflow entrance 11 for rotating.Further, the conveying of fluid can be carried out.Further, rotor part 20 can rotate non-contactly by the kinetic pressure of the first dynamic pressure groove 60 between rotor accommodating part 13 and axle portion 30.Because rotor part 20 rotates non-contactly, therefore, it is possible to reduce the damage of convection cell or go bad.Further, owing to there is no the contact wear in rotor part 20, rotor accommodating part 13 and axle portion 30, therefore, it is possible to reduce the generation of dust.
In the present embodiment, multiple man type chute and multiple spiral fluted groove width ratio wide with mound identical.That is, the size ratio that the groove width of dynamic pressure groove group is wide with mound is in the circumferential 1:1.But size ratio is not limited to this.Such as, mound is wide also can be wider than groove width.In multiple man type chute, the groove width of reflex part 611 also can be narrower than the groove width of the end at least one place in outside dynamic pressure groove 612 and inner side dynamic pressure groove 613.Further, in upper axial hydrodynamic groove 62 and lower axial dynamic pressure groove 63, the groove width of rotor inner peripheral surface 22 side also can be narrower than the groove width of side, rotor outer periphery face 21.The wide size of groove width and mound is than also can suitably combine.The size wide due to mound combines than suitably, therefore improves the running accuracy of rotor part 20.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
Further, in the present embodiment, multiple man type chute and multiple spiral fluted groove depth are constant.That is, from the size of the groove depth an of end to the other end of a dynamic pressure groove be identical.But the size of groove depth is not limited to this.Such as, in a dynamic pressure groove, also groove depth can be changed.Such as, in multiple man type chute, the groove depth of reflex part 611 also can be more shallow than the groove depth of the end at least one place in outside dynamic pressure groove 612 and inner side dynamic pressure groove 613.Further, in upper axial hydrodynamic groove 62 and lower axial dynamic pressure groove 63, the groove depth of rotor inner peripheral surface 22 side also can be more shallow than the groove depth of side, rotor outer periphery face 21.The size of groove depth also can suitably combine.Due to size appropriately combined of groove depth, therefore improve the running accuracy of rotor part 20.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
Fig. 5 is the longitudinal section of the rotor accommodating part 13 represented in casing 10.In the present embodiment, the second dynamic pressure groove 70 is configured at the casing inner peripheral surface 131 of the inner side in rotor accommodating part 13.Second dynamic pressure groove 70 is multiple spiral chute.Fluid configures from inflow entrance 11 to the direction that outflow opening 12 is carried along when centered by running shaft 2, axle rotates rotor part by the second dynamic pressure groove 70.Second dynamic pressure groove 70 along inclined direction extends relative to central shaft.More preferably, the second dynamic pressure groove 70 is longer than the axial length of rotor part.Because the second dynamic pressure groove 70 is longer than the axial length of rotor part, therefore carry the active area of the power of pumping of fluid large, can discharge pressure be improved.
Fig. 6 and Fig. 7 is the longitudinal section of the casing 10 of the variation of copying the second dynamic pressure groove 70.As shown in Figure 6 and Figure 7, the second dynamic pressure groove 70A and 70B is the multiple man type chutes being circumferentially arranged in casing inner peripheral surface 131A and 131B.
As shown in Figure 6, the second dynamic pressure groove 70A is multiple man type chutes that dynamic pressure groove extends from reflex part 611A to different direction.More preferably, the length of the dynamic pressure groove of inflow entrance 11A is extended to than the dynamic pressure flute length extending to outflow opening 12A.When centered by running shaft 2A, axle rotates rotor part, because the length of the dynamic pressure groove extending to inflow entrance 11A is long, therefore, it is possible to fluid is carried from inflow entrance 11A to outflow opening 12A.Further, by confluxing in the kinetic pressure of the fluid of reflex part 611A, reducing rocking of rotor part, improving the running accuracy of rotor part.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
As shown in Figure 7, the second dynamic pressure groove 70B is multiple man type chutes that dynamic pressure groove extends from reflex part 611B to different direction.Further, the dynamic pressure groove extended along different direction is not connected by reflex part 611B.That is, mound part is formed at reflex part 611B.Compared with the shape being slot part with reflex part as shown in Figure 6, reflex part 611B, due to the gap turn narrow with rotor outer periphery face, therefore more improves kinetic pressure.Therefore, when running shaft 2B rotates as central shaft by rotor part, also reduce rocking of rotor part by the kinetic pressure of the fluid coming together in reflex part 611B, improve the running accuracy of rotor part.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
As shown in Figure 1, magnet 50 and the second dynamic pressure groove 70 are diametrically.Further, stator 40 and magnet 50 are diametrically.Because magnet 50, stator 40 and the second dynamic pressure groove 70 are mutual diametrically, therefore, it is possible to reduce axial height.
Fig. 8 is the longitudinal section of the pump 1C exemplified as variation.Motor part 20C has magnet 50C, the first dynamic pressure groove 60C and the second dynamic pressure groove 70C.Below be only described with not existing together of Fig. 1.
Magnet 50C is configured near the 21C of rotor outer periphery face.Further, magnet 50C and the second dynamic pressure groove 70C configures vertically side by side.In the present embodiment, magnet 50C is configured at than the position of the second dynamic pressure groove 70C by outflow opening 12C side.Further, magnet 50C also can be configured at than the position of the second dynamic pressure groove 70C by inflow entrance 11C side.A part of magnet 50C also can be overlapping in radial direction with the second dynamic pressure groove 70C.Magnet 50C, by configuring side by side vertically with the second dynamic pressure groove 70C, can reduce radial dimension.
As illustrated in figures 1 and 8, in rotor part, by changing the position of magnet and the second dynamic pressure groove, the axis of pump and the size of radial direction can be changed.Therefore, in the slimming of pump, in conjunction with the shape of electronic component etc., the pump of various sizes can be provided.
Fig. 9 is the longitudinal section of example as the pump 1D of variation.Rotor part 20D has rotor cylindrical part 25D and rotor tilt portion 26D.Further, rotor accommodating part 13D have in conjunction with the shape of rotor part 20D, with the outer circumferential face of rotor part 20D across the relative barrel surface in gap and plane of inclination.Magnet 50D is configured near the outer circumferential face of rotor cylindrical part 25D, and with stator 40D diametrically.Second dynamic pressure groove 70D is configured at the casing inner peripheral surface 131D of rotor accommodating part 13D.In the present embodiment, the second dynamic pressure groove 70D is configured at the plane of inclination of casing inner peripheral surface 131D.In addition, the second dynamic pressure groove 70D also can be configured at the barrel surface of casing inner peripheral surface 131D.Further, the second dynamic pressure groove 70D also can be configured at the rotor outer periphery face 21D as rotor tilt portion 26D.
The position opening that with the diameter dimension of the rotor tilt portion 26D little part of inflow entrance 11D in the 13D of rotor accommodating part is relative.When centered by running shaft 2D, axle rotates rotor part 20D, fluid is carried to the side that diameter dimension is large by the side little from the diameter dimension of rotor tilt portion 26D by the second dynamic pressure groove 70D.Further, along the shape of rotor tilt portion 26D, fluid is carried by the side large to diameter dimension by centrifugal force.That is, by the effect of the carrying capacity of the second dynamic pressure groove 70D and the centrifugal force of rotor tilt portion 26D, the discharge pressure of fluid can be improved.
In addition, in the present embodiment, magnet 50D and the second dynamic pressure groove 70D is arranged side by side vertically.But be not limited thereto, also can a part of magnet 50D overlapping diametrically with the second dynamic pressure groove 70D.In addition, magnet 50D also can be configured to the second dynamic pressure groove 70D diametrically opposed.Because magnet 50D and the second dynamic pressure groove 70D is overlapping diametrically, therefore the axial height of pump 1D can step-down.Further, when magnet 50D is configured to radially relative with the second dynamic pressure groove 70D, rotor part 20D also can not have rotor cylindrical part 25D.At this moment, the axial height of pump 1D can step-down.
Figure 10 is the longitudinal section of example as the pump 10E of variation.Below, be only described with not existing together of Fig. 1.
Axle portion 30E has two the axle outer circumferential face 31E tilted from the mode that tip side reduces towards central part side with outside dimension.Further, rotor part 20E has with axle outer circumferential face 31E across relative two the rotor inner peripheral surface 22E in gap.Rotor inner peripheral surface 22E is the face tilted from upper rotor surface 23E and rotor lower surface 24E towards the mode that central direction diminishes with internal diameter size.That is, axle outer circumferential face 31E and rotor inner peripheral surface 22E has the plane of inclination radially expanded towards upper rotor surface 23E or rotor lower surface 24E.Between two axle outer circumferential face 31E and between two rotor inner peripheral surface 22E, there is roughly barrel surface respectively.Further, also can not configure this barrel surface, and be connected respectively by two axle outer circumferential face 31E and two rotor inner peripheral surface 22E.
At least one place surface configuration first dynamic pressure groove 60E in the plane of inclination of the plane of inclination of axle outer circumferential face 31E and rotor inner peripheral surface 22E.In the present embodiment, the first dynamic pressure groove 60E is multiple man type chute.Multiple man type chute is configured to the fluid when axle rotates rotor part 20E centered by running shaft 2E and is come together in reflex part 611E.By coming together in the fluid of reflex part 611E, make the first dynamic pressure groove 60E produce radial dynamic pressure and thrust dynamic pressure power simultaneously.Therefore, rotor part 20E does not need to configure radial dynamic pressure groove and axial hydrodynamic groove respectively.Lineup's font groove group can play the dynamic pressure effect of radial dynamic pressure groove and axial hydrodynamic groove simultaneously.By configuring two dynamic pressure groove groups as multiple man type chute vertically, reducing rocking of rotor part 20E, improving the running accuracy of rotor part 20E.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
In addition, in the present embodiment, the shape that multiple man type chute is configured at two plane of inclination arranged side by side is vertically illustrated.But be not limited to this.Such as, also one group of dynamic pressure groove group can be arranged in the plane of inclination shown in Figure 10, another group dynamic pressure groove group has the dynamic pressure groove group being respectively radial dynamic pressure groove and axial hydrodynamic groove as shown in Figure 1.
The longitudinal section of the pump 1F of Figure 11 involved by the second mode of execution of the present invention.As shown in figure 11, the pump 1F of present embodiment has casing 10F, rotor part 20F and axle portion 30F.Below, be only described with not existing together of Fig. 1.
Casing 10F is and the housing for carrying the pipe of fluid to be connected.Casing 10F has the connection mouth be connected with pipe.Manage and deliver the fluid to the inflow entrance 11F of pump and the exhaust port 12F that fluid is discharged from pump is connected.Inflow entrance 11F and outflow opening 12F is with through in the mode of casing inner peripheral surface 131F opening respectively.But aperture position is not limited to this, also can any one in inflow entrance 11F and outflow opening 12F at internal surface 132F opening.
Inflow entrance 11F is through to rotor accommodating part 13F.Further, outflow opening 12F is through to rotor accommodating part 13F.That is, inflow entrance 11F is communicated with outflow opening 12F via rotor accommodating part 13F.
Rotor part 20F is in roughly cylindric, and rotor part 20F is axle centered by axle portion 30F, and inserts vertically for axle portion 30F.Further, rotor part 20F is configured at rotor accommodating part 13F.Magnet 50F is configured near the rotor outer periphery face 21F of rotor part 20F.Magnet 50F configures in the mode radially relative with stator 40F.That is, axle portion 30F, magnet 50F and stator 40F configure in mode radially overlapping respectively.
The surface at least one place in rotor outer periphery face 21F and casing inner peripheral surface 131F has the second dynamic pressure groove 70F.Further, the second dynamic pressure groove 70F also can in rotor outer periphery face 21F and the configuration of this two place of casing inner peripheral surface 131F.
Fluid is dispersed throughout the space of inflow entrance 11F, rotor accommodating part 13F and outflow opening 12F.By the rotation of rotor part 20F, produce at the second dynamic pressure groove 70F and pump effect, thus fluid can be carried from inflow entrance 11F to outflow opening 12F.Further, because rotor accommodating part 13F is full of by fluid, so produce kinetic pressure by the first dynamic pressure groove 60F between rotor part 20F and axle portion 30F and rotor accommodating part 13F.By the rotation of this kinetic pressure supporting rotor portion 20F.Rotor part 20F, by the dynamic pressure effect of the first dynamic pressure groove 60F and the second dynamic pressure groove 70F, rotates in a non-contact manner in the 13F of rotor accommodating part.Thus, rotor part 20F does not contact with axle portion 30F and casing 10F and rotates.Can provide rotor part 20F and axle portion 30F and casing 10F do not produce wearing and tearing, the pump of long-life.Further, by non-contact, damage can not be produced or do not make fluid produce rotten etc. and carry out the conveying of fluid by convection cell.Further, the width in the gap of axle outer circumferential face 31F and rotor inner peripheral surface 22F is narrower than the width in the gap of casing inner peripheral surface 131F and rotor outer periphery face 21F.Because the width in the gap of axle outer circumferential face 31F and rotor inner peripheral surface 22F is narrower than the width in the gap of casing inner peripheral surface 131F and rotor outer periphery face 21F, therefore reduce rocking of rotor part 20F, improve the running accuracy of rotor part 20F.By improving running accuracy, reducing the vibration of pump, also reducing the deviation of the flow be transferred.
Figure 12 is the sectional view of the rotor accommodating part 13F be illustrated in casing 10F.In the present embodiment, the second dynamic pressure groove 70F is configured at the casing inner peripheral surface 131F in the inside of rotor accommodating part 13F.Second dynamic pressure groove 70F is multiple man type chute, configures two groups of dynamic pressure groove groups vertically.These two groups of dynamic pressure groove groups circumferentially arrange respectively to different direction.Multiple man type chute has reflex part 611F.The reflex part 611F of preferred each dynamic pressure groove group is overlapping vertically with inflow entrance 11F and outflow opening 12F.
More particularly, the reflex part 611F of one group of dynamic pressure groove group is overlapping vertically with inflow entrance 11F.Further, when centered by running shaft 2F, axle rotates rotor part, one group of dynamic pressure groove group is configured with multiple man type chute in the mode with the effect introduced from inflow entrance 11F by fluid.
The reflex part 611F of another group dynamic pressure groove group is overlapping in the axial direction with outflow opening 12F.Further, when centered by running shaft 2F, axle rotates rotor part, another group dynamic pressure groove group is configured with multiple man type chute in the mode with the effect of being discharged from outflow opening 12F by fluid.That is, two groups of dynamic pressure groove groups have respectively from the inflow entrance 11F introducing effect of fluid and the effect from outflow opening 12F displacement fluids.More particularly, be configured at the rotation of dynamic pressure groove group by rotor part of inflow entrance 11F, fluid be introduced into the inner side of rotor accommodating part 13F along the dynamic pressure groove extended in the vertical direction from reflex part 611F.Further, be configured at the rotation of dynamic pressure groove group by rotor part of outflow opening 12F, fluid is come together in reflex part 611F along the dynamic pressure groove extended in the vertical direction from reflex part 611F.Because reflex part 611F is overlapping vertically with outflow opening 12F, therefore fluid is discharged by from outflow opening 12F.
In fig. 12, two groups of multiple man type chutes are configured with vertically.Also as shown in figure 13, only multiple man type chute can be configured in outflow opening 12G side.Further, also as shown in figure 14, only multiple man type chute can be configured in inflow entrance 11G side.
As shown in figure 15, the second dynamic pressure groove 70J is the man type chute that dynamic pressure groove extends from reflex part 611J to different direction.Further, the dynamic pressure groove extended to different direction does not connect at reflex part 611J place.That is, mound part is formed at reflex part 611J.Compared with the shape being slot part with the reflex part shown in Figure 12, reflex part 611J, due to the gap turn narrow between rotor outer periphery face, thus more improves kinetic pressure.Therefore, when rotor part rotates using running shaft as central shaft, improved the discharge pressure of fluid by the kinetic pressure of reflex part 611J.
In the present embodiment, to flow through the overpressure of outflow opening less than the maximum delivery pressure of the fluid produced in the second dynamic pressure groove for fluid.More preferably, pressure dependence is: (overpressure of inflow entrance)=(overpressure of outflow opening) < (the maximum delivery pressure by the second dynamic pressure groove produces).By making the overpressure of inflow entrance and outflow opening less than the discharge pressure produced by the second dynamic pressure groove, thus can carry reposefully.
By changing the rotating speed of rotor part, feed flow can be controlled.Such as, by improving the rotating speed of rotor part, increase produced by the second dynamic pressure groove pump power.Consequently, can discharge pressure be improved, increase feed flow.Further, by changing the groove number of the second dynamic pressure groove, also feed flow can be controlled.Such as, by increasing the groove number of the second dynamic pressure groove, increase produced by the second dynamic pressure groove pump power.Consequently, discharge pressure can be improved, to increase feed flow.These also can suitably combine.
In the present embodiment, the groove depth of the first dynamic pressure groove is equal with the groove depth of the second dynamic pressure groove, or more shallow than the groove depth of the second dynamic pressure groove.And the mound of the first dynamic pressure groove is wide wide equal with the mound of the second dynamic pressure groove, or the mound width of ratio the second dynamic pressure groove.By making the groove depth of the first dynamic pressure groove more shallow than the groove depth of the second dynamic pressure groove, can reduce the flow flowed into the first dynamic pressure groove, fluid more can to the second dynamic pressure groove conveying.Further, by making the mound width of the mound of the first dynamic pressure groove wide ratio second dynamic pressure groove, can reduce the flow flowed into the first dynamic pressure groove, fluid more can to the second dynamic pressure groove conveying.
In the present embodiment, the first dynamic pressure groove and the second dynamic pressure groove are made by using the electrochemical machining method of the electrode imitating groove shape.The degree of depth of this dynamic pressure groove and the size of width is made accurately by electrochemical machining method.Further, this dynamic pressure groove also can be made by cutting working method.Further, this dynamic pressure groove also can be made by the plastic deformation based on punching press etc.When casing or rotor part are resin material, also can form the shape of dynamic pressure groove in advance on the mould of resin forming, to make this dynamic pressure groove when ejection formation.Also suitably can combine these.
Further, pump of the present invention also may be used for the equipment except electronic component.Such as, the present invention is applicable to delivery of medicaments in medical equipment.
Further, about the detailed shape of casing and pump, also can be different from the shape shown by each figure of the application.
Further, also in the scope not producing contradiction, each key element occurred in above-mentioned mode of execution or variation suitably can be combined.
The present invention can be used in the refrigerant liquid such as carrying cooling electronic apparatus.
Claims (24)
1. a hydraulic bearing pump, has:
Axle portion, described axle portion extends along the vertical direction;
Rotor part, the periphery in described axle portion surrounds by described rotor part, and has magnet; And
Casing, described casing is connected with described axle portion, and described rotor part is contained in inside,
Described casing has:
Stator, described stator is relative with described magnet;
Rotor accommodating part, described rotor accommodating part holds described rotor part; And
Inflow entrance and outflow opening, described inflow entrance and the through described rotor accommodating part of described outflow opening,
The feature of described hydraulic bearing pump is,
The surface at least one place in described rotor part, described axle portion and described rotor accommodating part has the first dynamic pressure groove of the described rotor part rotation of supporting,
The surface at least one place in described rotor part and described rotor accommodating part has the second dynamic pressure groove carried from described inflow entrance to described outflow opening by fluid,
Described rotor part has through hole through vertically.
2. hydraulic bearing pump according to claim 1, is characterized in that,
Cylindrically, described rotor part is axle centered by described axle portion for described rotor part, and inserts vertically for described axle portion,
The surface at least one place in the axle outer circumferential face in described axle portion and the rotor inner peripheral surface of described rotor part has the radial dynamic pressure groove as described first dynamic pressure groove.
3. hydraulic bearing pump according to claim 1, is characterized in that,
Described rotor part is using described axle portion as central shaft and have the upper rotor surface orthogonal with described axle portion and rotor lower surface,
The surface at least one place in the internal surface of described upper rotor surface, described rotor lower surface and described rotor accommodating part has the axial hydrodynamic groove as described first dynamic pressure groove,
The surface opening at least one place of described through hole in described upper rotor surface and described rotor lower surface.
4. hydraulic bearing pump according to claim 1, is characterized in that,
Multiple spiral chute or multiple man type chute is formed at described second dynamic pressure groove.
5. hydraulic bearing pump according to claim 1, is characterized in that,
Described rotor part cylindrically, using described axle portion as central shaft, and insert vertically for described axle portion by described rotor part,
Described rotor part has:
Rotor inner peripheral surface, described rotor inner peripheral surface is relative with the axle outer circumferential face in described axle portion;
Rotor outer periphery face, described rotor outer periphery face is relative with the casing inner peripheral surface of described rotor accommodating part; And
Upper rotor surface and rotor lower surface, described upper rotor surface and described rotor lower surface orthogonal with described axle portion,
The surface opening at least one place of described through hole in described upper rotor surface and described rotor lower surface,
Described hydraulic bearing pump has:
Radial dynamic pressure groove, described radial dynamic pressure groove is configured at the surface at least one place in described axle outer circumferential face and described rotor inner peripheral surface;
Axial hydrodynamic groove, described axial hydrodynamic groove is configured at the surface at least one place in the internal surface of described rotor accommodating part, described upper rotor surface and described rotor lower surface; And
Described second dynamic pressure groove, described second dynamic pressure groove is configured at the surface at least one place in described casing inner peripheral surface and described rotor outer periphery face.
6. hydraulic bearing pump according to claim 5, is characterized in that,
Described radial dynamic pressure groove is the multiple spiral chutes carried to the direction of described rotor inner peripheral surface by described fluid.
7. hydraulic bearing pump according to claim 5, is characterized in that,
Described radial dynamic pressure groove is multiple man type chute,
The width in described axle outer circumferential face and the gap of described rotor inner peripheral surface is narrower than the width in the gap in described casing inner peripheral surface and described rotor outer periphery face.
8. hydraulic bearing pump according to claim 5, is characterized in that,
Described magnet is configured to radially relative relative to described central shaft with described second dynamic pressure groove.
9. hydraulic bearing pump according to claim 5, is characterized in that,
Described magnet and described second dynamic pressure groove configure vertically side by side.
10. hydraulic bearing pump according to claim 5, is characterized in that,
Described second dynamic pressure groove is multiple spiral chute,
Fluid configures from described inflow entrance to the direction that described outflow opening is carried along by the rotation of described rotor part by described spiral chute.
11. hydraulic bearing pumps according to claim 10, is characterized in that,
Described outflow opening and described inflow entrance respectively at described upper rotor surface and described rotor lower surface opening,
The aperture position of described through hole is positioned at the position leaning on central axis direction than described outflow opening and described inflow entrance.
12. hydraulic bearing pumps according to claim 5, is characterized in that,
Described second dynamic pressure groove is the multiple man type chutes circumferentially configured,
Described man type chute has two different spiral chutes of true dip direction and is positioned at the reflex part at described spiral fluted center.
13. hydraulic bearing pumps according to claim 12, is characterized in that,
Described outflow opening and described inflow entrance are respectively at described rotor outer periphery face opening.
14. hydraulic bearing pumps according to claim 13, is characterized in that,
Described second dynamic pressure groove is one group of described multiple man type chute configured in the circumferential,
Described reflex part is configured at the position with the superposition of end gap of described outflow opening or described inflow entrance.
15. hydraulic bearing pumps according to claim 13, is characterized in that,
Described second dynamic pressure groove is two groups of described multiple man type chutes configured in the circumferential, wherein,
The described reflex part of one group is configured at the position with the superposition of end gap of described outflow opening,
The described reflex part of another group is configured at the position with the superposition of end gap of described inflow entrance,
The sense of rotation of direction relative to described rotor part of turning back of reflex part described in two groups is respectively towards postive direction and opposite direction.
16. hydraulic bearing pumps according to claim 1, is characterized in that,
Described rotor part cylindrically, using described axle portion as central shaft, and insert vertically for described axle portion by described rotor part,
Described rotor part has:
Rotor inner peripheral surface, described rotor inner peripheral surface is relative with the axle outer circumferential face in described axle portion;
Rotor outer periphery face, described rotor outer periphery face is relative with the casing inner peripheral surface of described rotor accommodating part; And
Upper rotor surface and rotor lower surface, described upper rotor surface and described rotor lower surface orthogonal with described axle portion,
Described axle outer circumferential face and described rotor inner peripheral surface have the plane of inclination radially expanded towards described upper rotor surface or described rotor lower surface,
Described first dynamic pressure groove is configured at the surface at least one place in the described plane of inclination of described axle outer circumferential face and the described plane of inclination of described rotor inner peripheral surface,
Described second dynamic pressure groove is configured at the surface at least one place in described casing inner peripheral surface and described rotor outer periphery face,
The surface opening at least one place of described through hole in described upper rotor surface and described rotor lower surface.
17. hydraulic bearing pumps according to claim 16, is characterized in that,
Described second dynamic pressure groove is multiple spiral chute,
Fluid configures from described inflow entrance to the direction that described outflow opening is carried along by the rotation of described rotor part by described spiral chute.
18. hydraulic bearing pumps according to claim 17, is characterized in that,
Described outflow opening and described inflow entrance respectively at described upper rotor surface and described rotor lower surface opening,
The aperture position of described through hole is positioned at the position leaning on central axis direction than described outflow opening and described inflow entrance.
19. hydraulic bearing pumps according to claim 16, is characterized in that,
Described second dynamic pressure groove is the multiple man type chutes circumferentially configured,
Described man type chute has two different spiral chutes of true dip direction and is positioned at the reflex part at described spiral fluted center.
20. hydraulic bearing pumps according to claim 19, is characterized in that,
Described outflow opening and described inflow entrance are respectively at described rotor outer periphery face opening.
21. hydraulic bearing pumps according to claim 20, is characterized in that,
Described second dynamic pressure groove is one group of described multiple man type chute configured in the circumferential,
Described reflex part is configured at the position with the superposition of end gap of described outflow opening or described inflow entrance.
22. hydraulic bearing pumps according to claim 20, is characterized in that,
Described second dynamic pressure groove is two groups of described multiple man type chutes configured in the circumferential, wherein,
The described reflex part of one group is positioned at the position with the superposition of end gap of described outflow opening,
The described reflex part of another group is positioned at the position with the superposition of end gap of described inflow entrance,
The described reflex part of two groups turn back direction relative to described rotor part sense of rotation respectively towards postive direction and in the other direction.
23. hydraulic bearing pumps according to any one of claim 1 to claim 22, is characterized in that,
The overpressure flowing through the fluid of described outflow opening is less than the maximum delivery pressure of the fluid produced in described second dynamic pressure groove.
24. hydraulic bearing pumps according to claim 23, is characterized in that,
The groove depth of described first dynamic pressure groove is identical with the groove depth of described second dynamic pressure groove, or more shallow than the groove depth of described second dynamic pressure groove,
Described in the Qiu Kuanyu of described first dynamic pressure groove, the mound of the second dynamic pressure groove is wide identical, or than the mound width of described second dynamic pressure groove.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
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| JP2014-169792 | 2014-08-22 | ||
| JP2014169792 | 2014-08-22 | ||
| JP2015-125604 | 2015-06-23 | ||
| JP2015125604A JP2016044673A (en) | 2014-08-22 | 2015-06-23 | Dynamic pressure bearing pump |
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| CN105370580A true CN105370580A (en) | 2016-03-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510464508.1A Pending CN105370580A (en) | 2014-08-22 | 2015-07-31 | Dynamic pressure bearing pump |
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| US (1) | US20160053769A1 (en) |
| JP (1) | JP2016044673A (en) |
| CN (1) | CN105370580A (en) |
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| JP2016044674A (en) * | 2014-08-22 | 2016-04-04 | 日本電産株式会社 | Dynamic pressure bearing pump |
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- 2015-06-23 JP JP2015125604A patent/JP2016044673A/en active Pending
- 2015-07-31 CN CN201510464508.1A patent/CN105370580A/en active Pending
- 2015-08-07 US US14/820,675 patent/US20160053769A1/en not_active Abandoned
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105386981A (en) * | 2014-08-22 | 2016-03-09 | 日本电产株式会社 | Dynamic pressure bearing pump |
| CN105833368A (en) * | 2016-05-11 | 2016-08-10 | 北京精密机电控制设备研究所 | Centrifugal impeller for blood pump |
| CN108799324A (en) * | 2017-04-27 | 2018-11-13 | 日本电产株式会社 | Hydrodynamic bearing device, motor and disk drive device |
| CN108525039A (en) * | 2018-05-14 | 2018-09-14 | 苏州心擎医疗技术有限公司 | Pump installation |
| CN110075377A (en) * | 2019-06-26 | 2019-08-02 | 上海微创医疗器械（集团）有限公司 | Magnetic liquid suspension formula blood pump |
| CN110075377B (en) * | 2019-06-26 | 2019-10-08 | 上海微创医疗器械（集团）有限公司 | Magnetic liquid suspension formula blood pump |
| CN112510865A (en) * | 2019-09-13 | 2021-03-16 | 通用汽车环球科技运作有限责任公司 | Method for reducing oil shear resistance in air gaps |
Also Published As
| Publication number | Publication date |
|---|---|
| US20160053769A1 (en) | 2016-02-25 |
| JP2016044673A (en) | 2016-04-04 |
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