CN110073120A - Bearing construction and motor compressor - Google Patents
Bearing construction and motor compressor Download PDFInfo
- Publication number
- CN110073120A CN110073120A CN201880004998.9A CN201880004998A CN110073120A CN 110073120 A CN110073120 A CN 110073120A CN 201880004998 A CN201880004998 A CN 201880004998A CN 110073120 A CN110073120 A CN 110073120A
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- China
- Prior art keywords
- ring
- bearing
- shell
- rotary shaft
- peripheral surface
- Prior art date
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Classifications
-
- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/059—Roller bearings
-
- 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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
- F16C27/066—Ball or roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Supercharger (AREA)
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The present invention relates to bearing construction and motor compressor, bearing construction of the invention has: rotary shaft；Bearing is installed in shell and relative to outer casing supporting rotary shaft, which includes inner ring, is inserted for rotary shaft；Outer ring comprising in the cricoid groove portion that the outer peripheral surface of the inner wall in face of shell is formed；O-ring is configured at the groove portion of the outer ring of bearing, and the inner wall prominent and with shell by radial outside to the position than outer peripheral surface abuts.Gap is formed between the inner wall of shell and the outer peripheral surface of bearing.The radial displacement of gap-ratio o-ring is big.
Description
Technical field
The present invention relates to bearing construction and motor compressors.
Background technique
In the past, there is known the bearing constructions that patent document 1,2 is recorded.Bearing construction described in Patent Document 1 has bearing
The bearing of the axis of fan motor.Slot in the outer ring of bearing is equipped with o-ring.O-ring is contacted with shell.Two o-rings it
Between be filled with viscous fluid.Bearing construction described in Patent Document 2 has the bearing of bearing drive shaft.Slot in the outer ring of bearing
O-ring is installed.Outer diameter face in outer ring is coated with heavy oil.
Patent document 1: Japanese Unexamined Patent Publication 2000-120669 bulletin
Patent document 2: Japanese Unexamined Patent Publication 2007-211865 bulletin
In bearing construction described in Patent Document 1, so that bearing is inserted when being equipped with the bearing group of o-ring loaded on shell
The mode for entering power reduction, sets the flattening surplus of o-ring.The insertion force is radial by the flattening surplus generation by o-ring
Power and coefficient of friction determine.I.e., by reducing radial power, and insertion force is made to become smaller.As a result, bearing operation when assembled
Property is good.In bearing construction described in Patent Document 2, the coefficient of friction between the aperture surface of shell and the outer diameter face of outer ring subtracts
It is small, thus prevent outer ring from attempting the creep rolled along the aperture surface of shell.
It is above-mentioned in the prior art, it is possible to the vibration of rotary body can not be prevented securely from via bearing and be passed to shell
It passs.If such as cause the outer ring of bearing to contact with shell because of vibration, vibration more transmitted.The present invention is to can be practical
Ground is prevented from vibrating via bearing and is illustrated to the bearing construction that shell transmits.
Summary of the invention
One embodiment of the present invention is a kind of bearing construction, and the rotary shaft of the rotary body for that will be accommodated in shell is opposite
It is supported in shell, wherein have: rotary shaft；Bearing, is installed in shell and relative to outer casing supporting rotary shaft, should
Bearing includes inner ring, inserts for rotary shaft；Outer ring comprising in the ring-type that the outer peripheral surface of the inner wall in face of shell is formed
Groove portion；And o-ring, it is configured at the groove portion of the outer ring of bearing, it is prominent simultaneously by radial outside to the position than outer peripheral surface
It is abutted with the inner wall of shell, gap, the diameter of gap-ratio o-ring is formed between the inner wall of shell and the outer peripheral surface of bearing
To displacement it is big.
According to one method of the present invention, vibration can be prevented securely to transmit via bearing to shell.
Detailed description of the invention
Fig. 1 is the cross-sectional view for indicating the motor compressor of an embodiment of the invention.
Fig. 2 is the cross-sectional view for indicating a part amplification of the bearing construction in Fig. 1.
(a) of Fig. 3 is the figure of the flattening surplus for indicating o-ring and the relationship of o-ring reaction force,
(b) of Fig. 3 is the figure for indicating the relationship of flattening surplus in gap and o-ring.
(a) of Fig. 4 is the figure for indicating the relationship in gap and o-ring reaction force, and (b) of Fig. 4 is to indicate gap and o-ring
Spring constant relationship figure.
Fig. 5 is the figure for indicating the relationship in gap and load displacement amount.
(a) of Fig. 6 is the figure for indicating the range in gap for the rotation stopping function that o-ring can be made to generate outer ring, (b) of Fig. 6
It is the figure for indicating to be prevented securely from the range in the gap of the transmitting of vibration.
Fig. 7 be by the figure after (b) of Fig. 6 (a) and Fig. 6 overlapping, be indicate can to get both prevent vibration transmitting and
The figure of the range in the gap of the rotation stop of outer ring.
Specific embodiment
One embodiment of the present invention is a kind of bearing construction, and the rotary shaft of the rotary body for that will be accommodated in shell is opposite
It is supported in shell, wherein have: rotary shaft；Bearing, is installed in shell and relative to outer casing supporting rotary shaft, should
Bearing includes inner ring, inserts for rotary shaft；Outer ring comprising in the ring-type that the outer peripheral surface of the inner wall in face of shell is formed
Groove portion；And o-ring, it is configured at the groove portion of the outer ring of bearing, it is prominent simultaneously by radial outside to the position than outer peripheral surface
It is abutted with the inner wall of shell, gap, the diameter of gap-ratio o-ring is formed between the inner wall of shell and the outer peripheral surface of bearing
To displacement it is big.
According to the bearing construction, the rotary shaft of rotary body is supported by bearing construction.It is set to outer ring and the shell of bearing
O-ring between inner wall plays the role of identical with spring.If rotary body rotates, quality and o-ring based on rotary body
Spring constant determine radial displacement.The gap being formed between the inner wall of shell and the outer peripheral surface of bearing is greater than O
The radial displacement of type ring, therefore prevent the outer ring of bearing from contacting with shell.According to the bearing construction, can be prevented securely from
Vibration is transmitted via bearing to shell.
In several embodiments, the inner wall of shell, bearing and o-ring are constituted are as follows: the inner wall and o-ring of shell
Between frictional force be greater than rotary body rotary force.In this case, in the case where rotary body rotates, it is able to suppress bearing
Outer ring rotation.
The motor compressor of other embodiments of the invention has: shell；Compressor impeller is installed on rotary shaft
End and a part for becoming rotary body；And bearing construction of any of claims 1 or 2, it is used for relative to shell bearing
Rotary shaft.According to the motor compressor, in the case where including the rotary body rotation of compressor impeller, prevent the outer ring of bearing with
Shell contact.Therefore vibration can be prevented securely to transmit via bearing and to shell, result is able to suppress motor compressor
Vibration, noise generation.
Hereinafter, on one side referring to attached drawing, while embodiments of the present invention will be described.In addition, in the description of the drawings
The same symbol is marked to identical element, and the repetitive description thereof will be omitted.In the following description, it is being known as " axial direction " or " radial direction "
In the case where, it is on the basis of rotary shaft 12.
The motor compressor of an embodiment is illustrated referring to Fig.1.Motor compressor 1 for example applied to vehicle,
The internal combustion engine of ship.Motor compressor 1 has compressor 7.Motor compressor 1 passes through the phase interaction of rotor portions 13 and stator department 14
With and make compressor impeller 8 rotate, the fluids such as air are compressed, generate compressed air.
Motor compressor 1 can also for example be connect with the booster (not shown) for the internal combustion engine for being applied to vehicle, ship.?
In this case, motor compressor 1 is to compression fluids such as the compressor conveying compressed airs of booster.Pass through combination motor compressor
1 and booster, the thus starting of 1 hydraulic booster of motor compressor.
Motor compressor 1 has: being supported to the rotary shaft 12 that can be rotated in shell 2 and is anchored on rotary shaft 12
Front end 12a compressor impeller 8.Shell 2 has: the motor case 3 and closing of storage rotor portions 13 and stator department 14
The end wall 3a of the opening of the second end side (diagram right side, the side opposite with compressor impeller 8) of motor case 3.Outside motor
The first end side (diagram left side, 8 side of compressor impeller) of shell 3 is provided with the compressor case 6 of storage compressor impeller 8.Compression
Machine shell 6 includes suction inlet 9, rolled portion 10 and outlet 11.The outside of end wall 3a for example also can be set for
The inverter 19 of the supply electric current of stator department 14.
Rotor portions 13 are installed on the axial central portion of rotary shaft 12, including being installed on the one or more of rotary shaft 12 forever
Long magnet (not shown).Stator department 14 is installed on the inner surface of motor case 3, including coil part in a manner of surrounding rotor portions 13
(not shown).If flowing alternating current in the coil part of stator department 14, the phase interaction of rotor portions 13 and stator department 14 is utilized
With rotating rotary shaft 12 integrally centered on rotation axis A with compressor impeller 8.If compressor impeller 8 rotates, press
Contracting machine 7 sucks external air by suction inlet 9, and compressed air is discharged by 10 compressed air of rolled portion, and from outlet 11.
The compressed air being discharged from outlet 11 is supplied to above-mentioned internal combustion engine.
Motor compressor 1 has two bearings 20 for capableing of rotatably supporting rotating shaft 12 relative to shell 2.Bearing 20 is pacified
In motor case 3 loaded on shell 2.Bearing 20 supports rotary shaft 12 with double base relative to motor case 3.First
Bearing 20 is set to the sleeve part 17 in the formation of 8 side of compressor impeller of motor case 3.Second bearing 20 is set to from end wall 3a
Along axial (8 side of compressor impeller) sleeve part 18 outstanding.Such as compressor impeller 8 is by being set to the front end of rotary shaft 12
The shaft end nut 16 of 12a and be installed on rotary shaft 12.
Rotary shaft 12, the compressor impeller 8 for being fixed on rotary shaft 12, rotor portions 13 and bearing 20 become in shell 2
Integrally constitute rotary body C.Rotary shaft 12, compressor impeller 8, rotor portions 13 and bearing 20 respectively become the one of rotary body C
Part.In the state of being accommodated in motor case 3, side's rotary body C in the axial direction exerts a force.The circular wall of sleeve part 17
Axial end face and abutting of the face 17b (referring to Fig. 2) in face of bearing 20, thus carry out the positioning of axial rotary body C.
In the motor compressor 1 of present embodiment, realizes and inhibit the issuable vibration because of the rotation of rotary body C
It is dynamic.In more detail, prevent the vibration of rotary body C relative to the transmitting of shell 2, result inhibits the vibration of motor compressor 1.
The transmitting vibrated in order to prevent, motor compressor 1 have the bearing construction including above-mentioned bearing 20.It is set relative to rotary shaft 12
It is placed in the bearing construction composition having the same of two axial positions.Each bearing construction is supported relative to motor case 3 to be rotated
The rotary shaft 12 of body C.
Hereinafter, being illustrated to the first bearing 20 and bearing construction that are set to the first end side.It omits to being set to the
The second bearing 20 of two end sides and the explanation of bearing construction.Second bearing 20 can also be with relative to the configuration of sleeve part 18
One bearing 20 is identical relative to the configuration of sleeve part 17.
Bearing 20 is, for example, ball bearing.More specifically, bearing 20 is, for example, grease lubrication formula transverse bearing.Bearing 20
It can be deep-groovebearing, be also possible to thrust bearing.
As shown in Fig. 2, bearing 20 includes: the inner ring 21 inserted for rotary shaft 12 and can be relative to via multiple balls 23
The outer ring 22 of 21 relative rotation of inner ring.Inner ring 21 is for example pressed into rotary shaft 12.The inner peripheral surface 21a of inner ring 21 and rotary shaft 12
Outer peripheral surface 12b is abutted.It the end face of 8 side of compressor impeller of inner ring 21 can also be with the protrusion 8a of compressor impeller 8 and rotation
Shaft axis A vertical end face abuts.
The sleeve part 17 of above-mentioned motor case 3 includes the cylindric inner peripheral surface (inner wall) towards radial inside
17a.17 supporting outer ring 22 of sleeve part.Outer ring 22 includes: the outer peripheral surface 22a of the inner peripheral surface 17a in face of sleeve part 17 and is formed in
The circular groove portion 22c of two of outer peripheral surface 22a.Inner peripheral surface 17a of the diameter of the outer peripheral surface 22a of outer ring 22 than sleeve part 17
It is small.Cylindric gap B is for example formed between the inner peripheral surface 17a of sleeve part 17 and the outer peripheral surface 22a of outer ring 22.Outer ring 22
8 side of compressor impeller end face can also with the annulus of the peripheral side for the protrusion 8a for being configured at compressor impeller 8 with
Rotation axis A vertical wall surface 17b is abutted.In addition, the shape of gap B motor compressor 1 operate when, can be according to rotary body
The displacement of C and change.
Two groove portion 22c are formed as separating in the axial direction.Each groove portion 22c and outer peripheral surface 22a are continuous, and towards radial outer
Side is open.In each groove portion 22c configured with circular o-ring 30.O-ring 30 is directly embedded into outer ring 22.O-ring 30 is by elastic material
Material is constituted.O-ring 30 is, for example, rubber system.The inner peripheral surface for being embedded in the o-ring 30 of groove portion 22c is abutted with the bottom surface of groove portion 22c.
A part of the peripheral side of o-ring 30 is more prominent to radial outside than the position of outer peripheral surface 22a.Distance rotation in o-ring 30
Axis A farthest circular peripheral end face, abuts with the inner peripheral surface 17a of sleeve part 17.
Nature (not shape by any external force of the o-ring 30 before being configured between bearing 20 and sleeve part 17
State) under, such as with circular section.The o-ring 30 clipped by the inner peripheral surface 17a of the groove portion 22c of bearing 20 and sleeve part 17
Compressed (flattening).Compressed o-ring 30 is for example with non-circular section.The size of above-mentioned gap B considers o-ring 30
The diameter (line footpath) of section, the flattening surplus of o-ring 30 and compressed o-ring 30 spring performance set.Gap
The size of B is not limited to above-mentioned element, such as it is also contemplated that the hardness (hard degree) of o-ring 30 is set.In addition " more than flattening
Amount " term be and " flattening amount " or " flattening ratio " identical concept.The term of " flattening " is identical concept with " compression ".
The considerations of referring to Fig. 3~Fig. 7 to the size of gap B, method was illustrated.Firstly, being examined as shown in (a) of Fig. 3
In the case where three kinds of line footpaths for having considered o-ring 30, even identical flattening surplus, reaction force is also because of line footpath, internal diameter, hardness
And it is different.The slope of each curve near tangent L shown in (a) of Fig. 3 is the spring constant of o-ring 30.
The relationship is indicated with formula below (1).
[formula 1]
F=π * κ/D*d0* (ax2+bx+c)...(1)
Here,
The reaction force of F:O type ring 30
The flattening surplus of x:O type ring 30
A, the coefficient when line footpath 1mm of b, c:O type ring 30 (wherein, coefficient is different due tos material and/or hardness etc.)
The line footpath of D:O type ring 30
The diameter of d0:O type ring 30
κ: coefficient.
Here, the size relationship of the flattening surplus x of o-ring 30 according to Fig.2, is indicated with formula below (2).
[formula 2]
Here,
X: the diameter of the bottom surface of groove portion 22c
Y: the internal diameter of sleeve part 17.
The size relationship of the radial size δ of gap B also according to Fig.2, is indicated with formula below (3).
[formula 3]
Here,
Z: the outer diameter (diameter of outer peripheral surface 22a) of outer ring 22.
By formula (2) and formula (3), the relationship of the flattening surplus x of the radial size δ and o-ring 30 of gap B is used
Formula (4) below indicates.
[formula 4]
/ 2 (4) x=D- (Y-X)/2=D- (2* δ+Z-X)
Here, the value of the outer diameter Z in the line footpath D and outer ring 22 for the diameter X, o-ring 30 for determining the seat surface of groove portion 22c
In the case where, formula (4) is such as shown in (b) of Fig. 3.In addition, in Fig. 2 referring to attached drawing in a manner of being easy imagination construction, to pressure
The o-ring 30 of state after contracting shows line footpath D, but strictly speaking this is inaccurate.Line footpath D is the o-ring 30 of nature
The diameter of linear parts.In addition size X, Y and Z are the diameter on the basis of rotation axis A respectively.
As shown in (b) of Fig. 3, if the radial size δ of gap B becomes larger, the flattening surplus x of o-ring 30 becomes smaller.Separately
Outside, the relationship of (b) of the relationship and Fig. 3 of (a) based on Fig. 3, as shown in (a) of Fig. 4, if the radial size δ of gap B becomes
Greatly, then the spring force of o-ring 30 becomes smaller.In addition, the frictional force Fr between o-ring 30 and the inner peripheral surface 17a of sleeve part 17 is O-shaped
The friction coefficient μ and rotary shaft 12 of ring 30 overcome the product of the resistance of the spring force F of o-ring 30.If therefore spring force F becomes smaller,
Then frictional force Fr also becomes smaller.
On the other hand, by by the rotation of rotary shaft 12 bearing 20 inner ring 21 and outer ring 22 boundary portion generate
The friction torque T of direction of rotationfIt is worth obtained from the radius R on the basis of rotation axis A divided by the outer peripheral surface 22a of outer ring 22
As rotary force Ft.Friction torque TfOther than the revolving speed of rotary shaft 12, additionally it is possible to according to the sticky ν of lubricating grease, rolling
Body rolling friction etc. and change.
Here, in order to make outer ring 22 (and o-ring 30) non-rotary condition be frictional force Fr bigger than rotary force Ft.That is,
The establishment of following formula (5) is first condition.
[formula 5]
Fr/Ft > 1 (5)
Inner peripheral surface 17a, bearing 20 and the o-ring 30 of the sleeve part 17 of motor case 3 are constituted are as follows: inner circumferential surface 17a and O
Frictional force Fr between type ring 30 is bigger than the rotary force Ft of rotary body C.In (a) of Fig. 6, becoming 1.0 or more gap model
When enclosing, the related rotation phenomenon of outer ring 22 is prevented.
On the other hand, spring constant K is the slope (i.e. the differential of formula (1)) of formula (1), therefore formula below (6)
It sets up.
[formula 6]
K=π * K/D*d0* (2ax+b) (6)
Here, according to the relationship (formula (4)) of (b) of Fig. 3, if the radial size δ of gap B becomes larger, o-ring 30
Surplus x is flattened to become smaller.In addition, if the flattening surplus x of o-ring 30 becomes smaller, spring constant K becomes smaller according to formula (6).Therefore
As shown in (b) of Fig. 4, if gap B (size δ) becomes larger, spring constant K becomes smaller.
Displacement r is according to M*g*r=1/2*K*r2Relationship, with formula below (7) indicate.
[formula 7]
Here,
The spring constant of K:O type ring 30
Mg: it is applied to the load (rotor quality load+eccentric load+oscillating load that bearing 20 is subject to etc.) of bearing 20
G: acceleration of gravity.
Formula (2) and formula (6) are substituted into formula (7), thus formula (8) below is set up.
[formula 8]
In order to make outer ring 22 without impinging on the condition of sleeve part 17 be gap B radial size δ it is bigger than displacement r.Therefore
According to formula (3) and formula (8), the establishment of formula (9) below becomes second condition.
[formula 9]
According to formula (9), as long as formula (10) is set up.
[formula 10]
This is as range indicated by an arrow in (b) of Fig. 6.
As shown in (a) of Fig. 4, even if load is identical, if gap B becomes larger, spring force becomes smaller, and is accompanied by this, load position
Shifting amount becomes larger.As shown in figure 5, producing load in the case where the size δ of displacement r (load displacement amount) than gap B is big
When displacement, the outer peripheral surface 22a of the outer ring 22 of bearing 20 is abutted with the inner peripheral surface 17a of sleeve part 17.This can become vibration, noise
The reason of.
Therefore, if relationship (second condition) shown in formula (10) set up, the outer peripheral surface 22a of outer ring 22 not with sleeve part
17 inner peripheral surface 17a is abutted.
Moreover, as shown in (a) of Fig. 6, according to above-mentioned first condition, in order to make o-ring 30 as the rotation stop of outer ring 22
It functions, the range needs in gap are the ranges being indicated by arrows in Fig..In addition, as shown in (b) of Fig. 6, according to above-mentioned the
Two conditions, in order to effectively inhibit vibration, the range needs in gap are the ranges being indicated by arrows in Fig..
According to (a) of Fig. 6 and (b) of Fig. 6, the rotation stop of first condition, that is, outer ring 22 and second condition are in order to balance
Inhibit vibration, sets the gap B of range indicated by an arrow in Fig. 7.In the present embodiment, spin load is considered in this way and is applied
It is added on the load of o-ring 30, the size δ of gap B is set in the range taken into account rotation stop and inhibit vibration.Taking into account them, this point is
The feature of present embodiment.
According to the present embodiment, the rotary shaft 12 of rotary body C is supported by bearing construction.Be set to the outer ring 22 of bearing 20 with
O-ring 30 between the inner peripheral surface 17a of motor case 3 can play the role of radial load identical with spring.If rotation
Body C rotation, then determine radial position based on the spring constant of the quality of rotary body C, eccentric load, vibration etc. and o-ring 30
Shifting amount.The gap B being formed between the inner peripheral surface 17a of shell 2 and the outer peripheral surface 22a of bearing 20, it is radial greater than o-ring 30
Displacement, therefore prevent the outer ring 22 of bearing 20 from contacting with sleeve part 17.According to the bearing construction, vibration can be prevented securely from
It is transmitted via bearing 20 to shell 2.Shock loading will not be applied to sleeve part 17, but apply the load buffered.
In above patent document, it was found that consider the spring force of o-ring and the document of rotating friction force.However, closing
It vibrated in inhibition, be conceived to the relationship in load displacement amount and gap to set this point of the flattening surplus of o-ring, then without any public affairs
It opens.In the present embodiment, it is conceived to above-mentioned two o'clock to set the flattening surplus of o-ring 30, can be realized and take into account reduction vibration
With the beneficial effect of rotation stopping function.
Frictional force between the inner peripheral surface 17a and o-ring 30 of shell 2 is greater than the rotary force of rotary body C, therefore in rotary body
In the case that C rotates, the outer ring 22 for being also able to suppress bearing 20 rotates.The electronic pressure that especially can sharp rise in revolving speed
In contracting machine 1, the rotation stop of outer ring 22 is important.
The outer of bearing 20 is prevented in the case where including the rotary body C rotation of compressor impeller 8 according to motor compressor 1
Circle 22 is contacted with shell 2.Therefore vibration can be prevented securely to transmit via bearing 20 and to shell 2, result is able to suppress
The vibration of motor compressor 1, the generation of noise.
More than, although embodiments of the present invention are illustrated, present invention is not limited to the embodiments described above.Example
Such as it is also possible to that two bearings 20 are arranged, and above-mentioned bearing construction is not provided with to one of those.Also two bearings be can be omitted
One in 20.In the case where bearing construction is only set to a position, bearing construction can also be only arranged at rotary shaft
12 the first end side can also be only arranged at the second end side of rotary shaft 12.
The relationship of the rotary force of frictional force and rotary body C between inner peripheral surface 17a and o-ring 30 can also be unsatisfactory for
State relationship shown in embodiment.Meet second condition although can also use but be unsatisfactory for bearing structure as first condition
It makes.In this case, the effect that vibration is transmitted to shell 2 can be prevented securely from by also realizing.
The section shape of o-ring 30 is not limited to circle.
Industrial utilizability
Several embodiments according to the present invention can be prevented securely from vibration and transmit via bearing to shell.
Description of symbols: 1 ... motor compressor；2 ... shells；3 ... motor cases；6 ... compressor cases；7 ... compressions
Machine；8 ... compressor impellers；12 ... rotary shafts；13 ... rotor portions；14 ... stator departments；17a ... inner peripheral surface (inner wall)；20 ... axis
It holds；21 ... inner rings；21a ... inner peripheral surface；22 ... outer rings；22a ... outer peripheral surface；22c ... groove portion；23 ... balls；3 ... o-rings；A ... rotation
Shaft axis；The gap B ...；C ... rotary body.
Claims (3)
1. a kind of bearing construction, for the rotary shaft for the rotary body being accommodated in shell to be supported relative to the shell,
It is characterized in that, having:
The rotary shaft；
Bearing is installed in the shell and relative to rotary shaft described in the outer casing supporting, which includes inner ring,
It is inserted for the rotary shaft；Outer ring comprising in the cricoid groove portion that the outer peripheral surface of the inner wall in face of the shell is formed；With
And
O-ring is configured at the groove portion of the outer ring of the bearing, to the position than the outer peripheral surface by the outer of radial direction
Side is prominent and abuts with the inner wall of the shell,
Gap is formed between the inner wall of the shell and the outer peripheral surface of the bearing, described in the gap-ratio
The radial displacement of o-ring is big.
2. bearing construction according to claim 1, which is characterized in that
The inner wall, the bearing and the o-ring of the shell are constituted are as follows: the inner wall of the shell and institute
State the rotary force that the frictional force between o-ring is greater than the rotary body.
3. a kind of motor compressor, which is characterized in that have:
The shell；
Compressor impeller is installed on the end of the rotary shaft and becomes a part of the rotary body；And
Bearing construction of any of claims 1 or 2 is used for relative to rotary shaft described in the outer casing supporting.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017-071204 | 2017-03-31 | ||
| JP2017071204 | 2017-03-31 | ||
| PCT/JP2018/012150 WO2018181186A1 (en) | 2017-03-31 | 2018-03-26 | Bearing structure and electric compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110073120A true CN110073120A (en) | 2019-07-30 |
Family
ID=63676107
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880004998.9A Pending CN110073120A (en) | 2017-03-31 | 2018-03-26 | Bearing construction and motor compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20200040903A1 (en) |
| JP (1) | JP6725064B2 (en) |
| CN (1) | CN110073120A (en) |
| DE (1) | DE112018001791T5 (en) |
| WO (1) | WO2018181186A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2563617B (en) * | 2017-06-20 | 2020-04-08 | Dyson Technology Ltd | An electric machine |
| CN112041573B (en) | 2018-04-27 | 2021-12-28 | 株式会社Ihi | Bearing and supercharger |
| JP2020148316A (en) * | 2019-03-15 | 2020-09-17 | Ntn株式会社 | Rolling bearing |
| DE102020210331A1 (en) | 2019-12-11 | 2021-06-17 | Efficient Energy Gmbh | Bearing holder for receiving a bearing |
| WO2021166136A1 (en) * | 2020-02-20 | 2021-08-26 | 三菱重工エンジン＆ターボチャージャ株式会社 | Compressor |
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| JP2005321006A (en) * | 2004-05-07 | 2005-11-17 | Nsk Ltd | Rolling bearing device |
| JP2006161876A (en) * | 2004-12-03 | 2006-06-22 | Nsk Ltd | Rolling bearing |
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| CN104508305A (en) * | 2012-08-28 | 2015-04-08 | 株式会社Ihi | Centrifugal compressor |
| JP2016148429A (en) * | 2015-02-13 | 2016-08-18 | 日本精工株式会社 | Friction roller type transmission |
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| JP2545028B2 (en) * | 1993-02-12 | 1996-10-16 | 川崎重工業株式会社 | Bearing device |
| JPH0989045A (en) * | 1995-09-27 | 1997-03-31 | Nec Eng Ltd | Shock absorbing support structure |
| JP2000120669A (en) | 1998-10-07 | 2000-04-25 | Nsk Ltd | Rolling bearing |
| JP4340145B2 (en) * | 2003-12-26 | 2009-10-07 | 株式会社日立製作所 | Anti-vibration tool holder |
| JP2007211865A (en) | 2006-02-08 | 2007-08-23 | Ntn Corp | Creep preventive roller bearing |
| JP2009190141A (en) * | 2008-02-15 | 2009-08-27 | Mitsubishi Heavy Ind Ltd | Machine tool and machining method |
-
2018
- 2018-03-26 US US16/492,375 patent/US20200040903A1/en not_active Abandoned
- 2018-03-26 CN CN201880004998.9A patent/CN110073120A/en active Pending
- 2018-03-26 DE DE112018001791.5T patent/DE112018001791T5/en active Pending
- 2018-03-26 WO PCT/JP2018/012150 patent/WO2018181186A1/en active Application Filing
- 2018-03-26 JP JP2019509808A patent/JP6725064B2/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005321006A (en) * | 2004-05-07 | 2005-11-17 | Nsk Ltd | Rolling bearing device |
| JP2006161876A (en) * | 2004-12-03 | 2006-06-22 | Nsk Ltd | Rolling bearing |
| JP2006234097A (en) * | 2005-02-25 | 2006-09-07 | Nsk Ltd | Creep prevention device and rolling bearing |
| CN101600890A (en) * | 2007-01-11 | 2009-12-09 | 日本精工株式会社 | Rolling bearing |
| JP2013124761A (en) * | 2011-12-16 | 2013-06-24 | Nsk Ltd | Rolling bearing |
| CN104508305A (en) * | 2012-08-28 | 2015-04-08 | 株式会社Ihi | Centrifugal compressor |
| JP2016148429A (en) * | 2015-02-13 | 2016-08-18 | 日本精工株式会社 | Friction roller type transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2018181186A1 (en) | 2018-10-04 |
| DE112018001791T5 (en) | 2019-12-12 |
| JP6725064B2 (en) | 2020-07-15 |
| US20200040903A1 (en) | 2020-02-06 |
| JPWO2018181186A1 (en) | 2019-07-04 |
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Application publication date: 20190730 |