CN106499634A - Motor compressor - Google Patents
Motor compressor Download PDFInfo
- Publication number
- CN106499634A CN106499634A CN201610590081.4A CN201610590081A CN106499634A CN 106499634 A CN106499634 A CN 106499634A CN 201610590081 A CN201610590081 A CN 201610590081A CN 106499634 A CN106499634 A CN 106499634A
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- China
- Prior art keywords
- tipper
- mentioned
- base bearing
- downside
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention provides a kind of performance and reliability high motor compressor.Base bearing (42) has：Slot segmentation (81) in the inner peripheral sliding surface of the segmentation up and down (42t) of the axial direction (G) of base bearing 42；In the upside tipper (82a) that the upside of the slot segmentation (81) of inner peripheral sliding surface (42t) is inclined relative to axial direction (G)；And the downside tipper (82b) inclined relative to axial direction (G) in the downside of the slot segmentation (81) of inner peripheral sliding surface (42t), upside tipper (82a) and downside tipper (82b) are formed as at least a portion when overlooking from axial direction (G) and overlap.
Description
Technical field
The present invention relates to motor compressor.
Background technology
Motor compressor is used for the refrigerating and air conditionings such as freezing-cooling storeroom, air conditioner and sets because compact and simple structure
Standby.In this motor compressor, the bearing fuel feeding to can support to swinging bent axle is needed.Patent documentation 1 describes one
Motor compressor is planted, its lower end for passing through the inner side for arranging the bearing (base bearing) from support bent axle is continuously inclined towards upper end
Groove (helicla flute) carries out fuel feeding come the whole region to base bearing.
Prior art literature
Patent documentation
Patent documentation 1：Japanese Unexamined Patent Publication 2010-255448 publications
Content of the invention
Invent problem to be solved
But, in the motor compressor that patent documentation 1 is recorded, since it is desired that continuous tipper is formed, so inclining
The angle of inclination of groove becomes big, and Wesco pump effect reduces, so as to due to causing because the fuel delivery to base bearing whole region is not enough
Bent axle contact with the metal of bearing, there is a possibility that performance and reliability reduce.
The present invention is for solving above-mentioned current problem, it is therefore intended that provide a kind of performance and reliability all high electronic
Compressor.
For solving the scheme of problem
It is a feature of the present invention that possessing：Motor；Compression mechanical part, which is had and is rotated using above-mentioned motor
The bent axle of driving and the bearing of above-mentioned bent axle is supported, and the sliding surface by above-mentioned bent axle with above-mentioned bearing is moistened using lubricating oil
Sliding；And incorporating section, which receives above-mentioned motor and compression mechanism section, and above-mentioned bearing and/or above-mentioned bent axle have：At least
One slot segmentation, its above-mentioned sliding surface of segmentation up and down in the axial direction of above-mentioned bearing；And tipper, which is relative to above-mentioned slip
The above-mentioned slot segmentation in face is located at above-mentioned axial upper and lower, and relative to above-mentioned axially inclined, each above-mentioned tipper is formed as,
When overlooking from above-mentioned axial direction, at least a portion is overlapped.
The effect of invention
In accordance with the invention it is possible to provide a kind of performance and reliability all high motor compressor.
Description of the drawings
Fig. 1 is the integrally-built longitudinal sectional view of the motor compressor for representing first embodiment.
Fig. 2 is the top view of the base bearing for representing motor compressor.
Fig. 3 is the line A-A sectional view of Fig. 1.
Fig. 4 is the action specification figure of compression mechanical part, (a) is 0 degree of situation, (b) is 90 degree of situation, (c) is 180 degree
Situation, (d) be 270 degree of situation.
Fig. 5 represents the base bearing of first embodiment, (a) is the line B-B sectional view of Fig. 2, (b) is the expansion of inner peripheral surface
Figure.
Fig. 6 represents the base bearing of comparative example 1, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
Fig. 7 represents the base bearing of comparative example 2, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
Fig. 8 represents the base bearing of comparative example 3, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
Fig. 9 represents the base bearing of second embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
Figure 10 represents the base bearing of the 3rd embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
Figure 11 represents the base bearing of the 4th embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
Figure 12 represents the base bearing of the 5th embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
The explanation of symbol
1 motor compressor, 2 hermetic containers (incorporating section), 3 motor, 4 compression mechanical parts, 5 accumulators,
5a suction pipes, 21 cylinders, 22 lids, 23 bottom bodies, 23a oil storage tanks, 31 stators, 32 rotors, 41 bent axles,
41a eccentric parts, 41b hollow bulbs, 42,42A, 42B, 42C, 42D base bearing (bearing), 42a end plates, 42b cylinders
Portion, 42e engravings portion, 42f floss holes, 42t inner peripheral sliding surfaces (sliding surface), 43 cylinders, 43a cylinder chamber, 44
Supplementary bearing, 45 rollers, 46 blades, 47 disc springs, 48 oiled-plate methods, 54 delivery pipes, 71 drain valves, 72 retainers,
73 cup-shaped deafeners, 81,81c, 81d, 81e, 81f slot segmentation, tipper (tipper) on the upside of 82a, 82c, 82e,
Tipper (tipper) on the downside of 82b, 82d, 82f, 82g, 82h, 82i tipper, G axial directions, Q1 suction chambers, Q2 are pressed
Contracting room, R1 direction of rotation, the flow direction of R2 oil.
Specific embodiment
Hereinafter, with reference to appropriate accompanying drawing, while to for implementing the mode (hereinafter referred to as " embodiment party of the present invention
Formula ") it is described in detail.Additionally, each scheme only to fully understand that the degree of the present invention is schematically illustrated.
Therefore, the present invention is not limited to embodiment described below.In addition, in the various figures, for common structural element, identical
Structural element, simultaneously the repetitive description thereof will be omitted for mark identical symbol.In addition, following, although lift as sealed electrical compressor
Example Rotary Compressor is illustrated, but is not limited to Rotary Compressor, it is also possible to be applied to scroll compressor, past
The motor compressors such as twin compressor.
(first embodiment)
Fig. 1 is the integrally-built longitudinal sectional view of the motor compressor for representing first embodiment.Additionally, Fig. 1 is only simple
The motor compressor 1 of explanation first embodiment necessary to part singly is shown.
As shown in figure 1, the motor compressor 1 of first embodiment possess hermetic container 2 (incorporating section), motor 3 and
Compression mechanical part 4 and constitute.
Hermetic container 2 is made up of cylinder 21, lid 22 and bottom body 23.Cylinder 21 is made up of steel plate, and is upper and lower opening
Cylindrical shape housing.Lid 22 is disk-shaped, and is fitted together in the way of blocking the upper opening of cylinder 21.Bottom body 23 is in disk
Shape, and be fitted together in the way of blocking the lower openings of cylinder 21.Lid 22 and bottom body 23 are welded in cylinder 21, so as to be formed
By structure closed for the inside of hermetic container 2.
Constitute hermetic container 2 bottom bottom body 23 upper surface (inner surface) be provided with storage freezer oil (lubricating oil,
Hereinafter referred to as oil) oil storage tank 23a.Refrigerator oil is supplied to compression mechanical part 4, to lubricate the sliding surface of compression mechanical part 4,
And the gap in portion of seal compression mechanism 4.
Motor 3 is the driving source for driving compression mechanical part 4, and which possesses by hot jacket etc. and is fixed on hermetic container 2
The stator 31 of inwall and constitute in the chimeric rotor 32 in the top of the bent axle 41 of compression mechanical part 4.
The structure of compression mechanical part 4 is, with motor 3 rotor 32 rotary motion to action fluid (cold-producing medium gas
Body) it is compressed, and the action fluid that have compressed is supplied to the freeze cycle of refrigerating and air conditioning machine.In addition, compression mechanical part 4
Possess with lower member and constituted：Bent axle 41, base bearing 42, cylinder 43, supplementary bearing 44, roller 45, blade 46 and disc spring 47.
Bent axle 41 is the part of the internal drive blade 46 in cylinder 43, and which has eccentric part 41a in lower end side.In addition,
Bent axle 41 passes through embedded for the side more top than eccentric part 41a base bearing 42, and will be embedded for the side than eccentric part 41a on the lower secondary
Bearing 44, and rotatably it is supported in the inside of hermetic container 2.
In addition, in bent axle 41, from the beginning of lower surface, the axial G along bent axle 41 (base bearing 42, supplementary bearing 44) is formed with
Hollow bulb 41b.Hollow bulb 41b is formed extend to the height and position of the lower end of base bearing 42.In addition, embedded in hollow bulb 41b
Conjunction has oiled-plate method 48.The oiled-plate method 48 has the shape for reversing thin plate on the direction of rotation of bent axle 41.Using oiled-plate method 48 with
Bent axle 41 to rotate, by centrifugal pump effect, the oil of the oil storage tank 23a of the bottom 53 of hermetic container 2 is attracted (drinking up), from
And fuel feeding is carried out to base bearing 42, supplementary bearing 44 and eccentric part 41a.
The hole that connects respectively is formed with the internal side diameter of base bearing 42, supplementary bearing 44 and roller 45 in bent axle 41 (not scheme
Show), the oil pumped by oiled-plate method 48 supplied by each hole to the internal diameter lower end of base bearing 42, supplementary bearing 44 internal diameter upper end with
And the internal side diameter of roller 45.
It is in that substantially discoidal end plate 42a extends with the radial center from end plate 42a upward that base bearing 42 possesses
Cylindrical portion 42b, and bent axle 41 is supported by cylindrical portion 42b.The periphery wall of end plate 42a is fixed on by welding etc.
The inner circumferential wall of the cylinder 21 of hermetic container 2.
In addition, floss hole 42f (with reference to Fig. 2) is formed with the end plate 42a of base bearing 42, and be provided with selectively opened or close
The drain valve 71 for closing floss hole 42f and the retainer 72 of the aperture (control is excessively opened) for determining drain valve 71.
Cylinder 43 has the through hole of the cylinder of insertion on axial G in radial center.By the through hole, base bearing
42 and supplementary bearing 44, constitute cylinder chamber's (through hole) 43a.In addition, cylinder 43 is by multiple bolt Bs (with reference to Fig. 3) and master
Bearing 42 is fastened.The upper surface of cylinder 43 is blocked by base bearing 42.
Supplementary bearing 44 possess blocking cylinder 43 lower surface end plate 44a and the radial center from end plate 44a downwards
Extend and support cylindrical portion 44b of the lower end of bent axle 41 and constitute.The length of the axial G of cylindrical portion 44b is formed as comparing cylindrical portion
42b is short.In addition, supplementary bearing 44 is fastened with cylinder 43 by bolt (not shown).
Roller 45 is formed as cylindric, and is configured at cylinder chamber 43a.In addition, the internal side diameter in roller 45 is embedded in the inclined of bent axle 41
Center portion 41a, roller 45 are configured to rotate freely in the outer circumferential side of eccentric part 41a.
Blade 46 is configured to the outer peripheral face for being connected to roller 45.In addition, blade 46 is plate shape, and it is configured in cylinder 43
Portion radially moves back and forth.
Disc spring 47 is configured at transverse holes 43b radially extended in cylinder 43.Disc spring 47 is supported with blade 46 by one end
Connect, the other end is embedded in transverse holes 43b and blade 46 is exerted a force towards roller 45.
In addition, being provided with accumulator 5 and by accumulator 5 from freeze cycle to compression mechanical part 4 in the outside of hermetic container 2
The suction pipe 5a of guiding action fluid.Accumulator 5 is that have as action fluid and the cold-producing medium of function using pressurized state savings
The container of gas.Suction pipe 5a is connected to the end of the suction inlet 43c (with reference to Fig. 3) connected with cylinder chamber 43a.
Fig. 2 is the top view of the base bearing for representing motor compressor.Additionally, Fig. 2 is to unload drain valve 71 from base bearing 42
The state of (with reference to Fig. 1) and retainer 72 (with reference to Fig. 1), is the state of base bearing viewed from above 42.
As shown in Fig. 2 on the end plate 42a of base bearing 42, around cylindrical portion 42b, with (reference picture on axial G
1) mode of insertion is formed with bolt fastening bolt insertion hole 42c in many places.Additionally, the number of bolt insertion hole 42c is not limited
Due to four, suitably can change.
In addition, in the outer circumferential side of end plate 42a, being formed with the elongated hole 42d in the upper insertions of axial G (with reference to Fig. 1) in many places.This
A little elongated hole 42d are for the oil being discharged in hermetic container 2 from compression mechanical part 4 (refrigerator oil) is back to oil storage tank 23a
Stream.
In addition, on end plate 42a, in the spill for being formed about installing drain valve 71 (with reference to Fig. 1) of cylindrical portion 42b
Engraving portion 42e.Engraving portion 42e is substantially long hole shape when overlooking, and bottom surface at one end is formed with refrigerant gas (action
Fluid) the floss hole 42f that discharges, it is formed with the bottom surface of the other end and (riveting) drain valve 71 is fixed with overhang (Fig. 1 joins
According to) fixed part (caulking part) 42g.
Fig. 3 is the line A-A sectional view of Fig. 1.When Fig. 3 is that the boundary member in base bearing 42 and cylinder 43 of Fig. 1 cuts off
Sectional view.
As shown in figure 3, being shaped as when overlooking of cylinder 43, with rounded portions 43m for forming cylinder chamber 43a and from the circle
The extension 43n that a part of shape portion 43m extends to the side of suction pipe 5a.
In addition, cylinder 43 is formed with slit 43d, slit 43d diametrically prolongs across rounded portions 43m and extension 43n
Stretch, and insert blade 46.
Blade 46 is embedded in the slit 43d of cylinder 43, and contact is being revolved with the eccentric motion of eccentric part 41a
On the periphery of the roller 45 for turning, motion of retreating is carried out.
Cylinder chamber 43a is formed with the discharge chambe for the suction chamber Q1 of suction action fluid and for compressed action fluid
Q2.Discharge chambe Q2 is by being formed with lower member：The internal face 43s of cylinder chamber 43a, outside wall surface 45s of roller 45, the side of blade 46
(side on diagram right side) 46s, the internal face 42s (with reference to Fig. 1) of base bearing 42 (end plate 42a) and 44 (end plate of supplementary bearing
Internal face 44s (with reference to Fig. 1) 44a).
In compression mechanical part 4, bent axle 41 is configured to be rotated by motor 3 (with reference to Fig. 1) in the direction of the arrow rl,
So as to pass through the reciprocating motion of the eccentric rotary and blade 46 of eccentric part 41a, the volume of suction chamber Q1 and discharge chambe Q2 is become
Change, and changed action liquid pressure rise by the volume.Gas pressure Pd1 (with reference to Fig. 1) and pressure in the inside of hermetic container 2
When the gas pressure Pd2 of the inside of contracting room Q2 is the relation of Pd2 >=Pd1, floss hole 42f (ginsengs opened by drain valve 71 (with reference to Fig. 1)
According to Fig. 2).So as to drain valve 71 makes the gases at high pressure (action fluid) of the inside of discharge chambe Q2 be ejected into the interior of hermetic container 2
Portion.In addition, when in addition, drain valve 71 cuts out floss hole 42f.So as to drain valve 71 prevents the interior of hermetic container 2
The gases at high pressure (action fluid) in portion are back to the inside of discharge chambe Q2.
Cup-shaped deafener 73 is configured to the dish type for covering drain valve 71 and retainer 72, and plays work(as acoustic filter
Energy.Additionally, being provided with for the action fluid discharged from floss hole 42f is emitted in hermetic container 2 in cup-shaped deafener 73
Discharge orifice (not shown).From cup-shaped deafener 73 be emitted into the refrigerant gas in hermetic container 2 by the gap of motor 3,
Pore (not shown), and the outside of hermetic container 2 is emitted into from the delivery pipe 54 (with reference to Fig. 1) located at the top of hermetic container 2
(freeze cycle).
Fig. 4 is the action specification figure of compression mechanical part, (a) is 0 degree of situation, (b) is 90 degree of situation, (c) is 180 degree
Situation, (d) be 270 degree of situation.
Blade 46 is retreated the inner most state of the slit 43d to cylinder 43 as 0 degree for Fig. 4 (a).In this case, gas
Cylinder chamber 43a generally sucks space, and the power of the compressive load of the extruding base bearing 42 of bent axle 41 does not work.
As shown in Fig. 4 (b), when eccentric part 41a is rotated by 90 ° in the counterclockwise direction from the state shown in Fig. 4 (a), become
A part for blade 46 is pushed out to the state in cylinder chamber 43a by the slit 43d from cylinder 43, by blade 46, is divided into suction
Enter the room and discharge chambe.In this case compressive load direction S1 is and links the contact P1 and roller 45 and cylinder of blade 46 and roller 45
The vertical direction of the straight line of 43 contact P2.In addition, being anti-compressive load with compressive load direction S1 into the contrary direction of 180 degree
Direction S2.
As shown in Fig. 4 (c), when eccentric part 41a rotates 180 degree in the counterclockwise direction from the state described in Fig. 4 (a), become
The state in cylinder chamber 43a is farthest pushed out to by the slit 43d from cylinder 43 into blade 46.In this case compression is born
It is the direction vertical with the straight line of the contact P4 of cylinder 43 with the contact P3 of roller 45 and roller 45 with blade 46 is linked to carry direction S3.Separately
Outward, it is back-pressure contracting load direction S4 with compressive load direction S3 into the contrary direction of 180 degree.
As described in Fig. 4 (d), when eccentric part 41a rotates 270 degree in the counterclockwise direction from the state shown in Fig. 4 (a), become
Into blade 46 in the way of a part is projected in cylinder chamber 43a from the slit 43d of cylinder 43 bulged-in state.In this case
Compressive load direction S5 be with link blade 46 vertical with the straight line of the contact P6 of cylinder 43 with the contact P5 of roller 45 and roller 45
Direction.In addition, being back-pressure contracting load direction S6 with compressive load direction S5 into the contrary direction of 180 degree.
In fluid lubrication system, prevent bent axle 41 from being contacted with base bearing 42 by oil film pressure, and be formed with groove
The part of (tipper) is the part of bent axle 41 and the gap increase of base bearing 42, and therefore oil film pressure is easy to escape.Therefore, if
Tipper is set in the range of～90 degree of -90 degree of the relative direction of compressive load direction S1, S3, S5 (negative compression is born
There is groove where load), then bent axle 41 and base bearing 42 become prone to contact.Therefore, in the present embodiment, by inclining
Groove is arranged at the anti-compressive load constituted outside the scope of～90 degree of -90 degree of the relative direction of compressive load direction S1, S3, S5
Face, is prevented from the contact of bent axle 41 and base bearing 42, it is possible to increase the performance and reliability of motor compressor 1.
Fig. 5 represents the base bearing of first embodiment, (a) is the line B-B sectional view of Fig. 2, (b) is expanded view.Additionally, figure
Angle shown in the transverse axis of 5 (b) with shown in Fig. 2 angle (0 degree, 90 degree, 180 degree, 270 degree) corresponding, being will be negative for back-pressure contracting
The end of section is set to the example of substantially 45 degree (gamut of back-pressure contracting load surface is set to substantially 135 degree).Additionally, for 45 degree
(135 degree), its according to model, operating condition and change, be not limited to present embodiment.
As shown in Fig. 5 (a), base bearing 42 has slot segmentation 81, upside tipper (tipper) 82a and downside tipper
(tipper) 82b, up and down segmentation inner peripheral sliding surface 42t (sliding surface) of the slot segmentation 81 in axial G (with reference to Fig. 1), upside inclines
Groove (tipper) 82a is located at the upside of slot segmentation 81, and inclines relative to axial G, and downside tipper (tipper) 82b is located at and divides
The downside of groove 81 is cut, and is inclined relative to axial G.
Slot segmentation 81 is located at the centre of the short transverse (axial G) of cylindrical portion 42b of base bearing 42, and is circumferentially formed at
Complete cycle.If additionally, slot segmentation 81 is formed with makes the upside oil circuits that connect with downside tipper 82b of tipper 82a, without formation
In complete cycle.
Upside tipper 82a is that the upper end 81a for making slot segmentation 81 is connected with the upper end 42h of base bearing 42 (cylindrical portion 42b)
Oil circuit, and relative to axial G incline.
Downside tipper 82b is that the lower end 81b for making slot segmentation 81 is connected with the lower end 42i of base bearing 42 (cylindrical portion 42b)
Oil circuit, and relative to axial G incline.
As shown in Fig. 5 (b), upside tipper 82a and downside tipper 82b is formed as mutual identical length and mutually puts down
OK.In addition, when overlooking from axial G, upside tipper 82a and downside tipper 82b are formed as overlapped.That is, upper inclination
One end of skewed slot 82a is the position of 270 degree when overlooking of base bearing 42, and the other end is 45 degree when overlooking of base bearing 42
Position.Similarly one end is 270 degree of position to downside tipper 82b, and the other end is 45 degree of position.So as to upside tipper
82a and downside tipper 82b both sides are respectively positioned in the range of above-mentioned back-pressure contracting load surface.
In addition, tipper 82a in upside is forming the direction of rotation R1 (with reference to Fig. 3) relative to bent axle 41 (relative to oil
Flow direction R2) incline in upstream side formation entrance, the mode for forming the direction for exporting in downstream.Downside tipper 82b with
Formed direction of rotation R1 (with reference to Fig. 3) (relative to the flow direction R2 of oil) relative to bent axle 41 downstream formed outlet,
The mode for forming the direction of entrance in upstream side is inclined.In addition, the entrance of upside tipper 82a is relative to direction of rotation R1 (oil
Flow direction R2) outlet upstream side than downside tipper 82b.So as to the oil that tipper 82b flows out in downside is along thin
The direction flowing that solid arrow is represented, is grown the circulation of (225 degree) in slot segmentation 81, then flows to upside tipper
82a, therefore, it is possible to effectively cooling base bearing 42.
Here, the Wesco pump effect to tipper (upside tipper 82a, downside tipper 82b) is illustrated.
For the fuel delivery that the Wesco pump effect by tipper is brought, if using fuel delivery Q [mm3/ min], axle radius R
[mm], rotating speed N [min-1], the sectional area A [mm of tipper2], tipper relative to direction of rotation level angle (below,
Referred to as inclination angle) θ [spending], then can be expressed by following formula (1).
Q=A π RNcos θ (1)
Here, the sectional area A [mm of tipper2] and tiltangleθ [spending] can set tipper when be adjusted, but
Sectional area A [the mm of tipper2] change with greater need for change cutter shape, therefore, it is difficult to arranging to the motor compressor of many specifications
Optimal tipper.In contrast, the change of tiltangleθ [spending] can be by changing the angle during processing as same tool
Etc. corresponding to, therefore in the case of consideration production efficiency, the adjustment of fuel delivery is expected that by tiltangleθ [spending] to carry out.
However, for the bending for suppressing the bent axle 41 caused because of the centrifugal force of rotor 32, relative to supplementary bearing 44, in axle
Base bearing 42 is lengthened on G, so as to slippage loss is easy to increase.Therefore, inner peripheral sliding surface 42t in base bearing 42 arranges segmentation
Groove 81 such that it is able to which the area of inner peripheral sliding surface 42t of base bearing 42 is down to the reliability for being able to ensure that bearing to compressive load
The minimum area of property, can realize the reduction of slippage loss.
In addition, Wesco pump effect of the oil (refrigerator oil) of the lower end supplied to base bearing 42 according to downside tipper 82b
It is attracted to slot segmentation 81.Slot segmentation 81 is arranged by inner peripheral sliding surface 42t in base bearing 42, the oil of attraction passes through slot segmentation
81, and oil is circulated in slot segmentation 81 such that it is able to cool down base bearing 42.Oil after cooling is again due to upside tipper
The Wesco pump effect of 82a and be attracted to the upper end of base bearing 42, and be finally discarded to the inside of hermetic container 2.
But, even for the structure that slot segmentation 81 is formed with base bearing 42, also produce the problem of described below.For
The point, the comparative example with reference to shown in Fig. 6 to Fig. 8 are illustrated.Fig. 6 represents the base bearing of comparative example 1, (a) is longitudinal sectional view,
B () is the expanded view of inner peripheral surface, Fig. 7 represents the base bearing of comparative example 2, (a) is longitudinal sectional view, (b) is the expansion of inner peripheral surface
Figure, Fig. 8 represents the base bearing of comparative example 3, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.Additionally, in Fig. 6 to Fig. 8
In, base bearing 100,110,120 is illustrate only, for other structures, is set to identical with first embodiment.
Base bearing 100 shown in Fig. 6 (a) possesses located at the upside tipper 101a of the upside of slot segmentation 81 and located at segmentation
The downside tipper 101b of the downside of groove 81.In addition, as shown in Fig. 6 (b), upside tipper 101a and downside tipper 101b shapes
Becoming.In other words, upside tipper 101a and downside tipper 101b are located along the same line
(on same spiral).
In the base bearing 100 of comparative example 1, the oil for being emitted into slot segmentation 81 from lower tilt groove 101b is present not in segmentation
Groove 81 is circulated and flows into the probability of upper angled groove 101a.Therefore, the circulation of the oil in slot segmentation 81 is damaged, and damages master
The cooling effect of bearing 42.If in addition, upper angled groove 101a and lower tilt groove 101b are formed as being included in anti-compressive load
In the range of face, then upper angled groove 101a and lower tilt groove 101b with the face (circumferencial direction) orthogonal with axial G as base
Accurate tilt angle theta 10 becomes big, and so as to Wesco pump effect reduces, fuel delivery reduces.
Base bearing 110 shown in Fig. 7 (a) possesses located at the upside tipper 110a of the upside of slot segmentation 81 and located at segmentation
The downside tipper 110b of the downside of groove 81.In addition, as shown in Fig. 7 (b), upside tipper 110a and downside tipper 110b shapes
Becoming.In other words, upside tipper 110a and downside tipper 110b are located along the same line
(on same spiral).
In the base bearing 110 of comparative example 2, the oil for being emitted into slot segmentation 81 from lower tilt groove 110b is present not in segmentation
81 interior circulation of groove and flow into the probability of upper angled groove 110a.Therefore, damage by slot segmentation 81 bring to the cold of bearing 110
But effect.If in addition, the tilt angle theta 1 of lower tilt groove 110b being set as, the tilt angle theta 10 than Fig. 6 (b) is little, on
Tipper 110a in portion departs from the scope of back-pressure contracting load surface, so as to improve bent axle 41 and base bearing 42 enters that row metal contacts can
Can property.
Base bearing 120 shown in Fig. 8 (a) is formed as on axial G than the base bearing 100 shown in Fig. 6 (a) and Fig. 7 (a) institutes
The base bearing 110 for showing is grown, and possesses the downside located at the upside tipper 120a of the upside of slot segmentation 81 and located at slot segmentation 81
Downside tipper 120b.In addition, as shown in Fig. 8 (b), upside tipper 120a and downside tipper 120b is formed as in axial direction
Do not overlap when overlooking on G.In other words, upside tipper 120a and downside tipper 120b are located along the same line (same spiral
On).
In the base bearing 120 of comparative example 3, the refrigerator oil for being emitted into slot segmentation 81 from lower tilt groove 120b is present not
It is circulated in slot segmentation 81 and flows into the probability of upper angled groove 120a.Therefore, damage by slot segmentation 81 bring to master
The cooling effect of bearing 120.If in addition, the tilt angle theta 10 of lower tilt groove 120b is set to the inclination angle with Fig. 6 (b)
θ 10 is identical for degree, then a part of upper angled groove 120a departs from the scope of back-pressure contracting load surface, improves bent axle 41 and base bearing
42 probabilities for entering row metal contact.
Therefore, the motor compressor 1 of first embodiment possesses the inner circumferential slip of the base bearing 42 of segmentation up and down in axial G
The slot segmentation 81 of face 42t, the upside tipper 82a inclined relative to axial G in the upside of slot segmentation 81 and in slot segmentation 81
The downside tipper 82b that inclines relative to axial G of downside.And, upside tipper 82a and downside tipper 82b are configured to,
When overlooking from the axial G of base bearing 42, at least a portion overlaps (being all overlaps in the first embodiment).Accordingly, with such as
It is located at upside tipper 100a, 110a, 120a and downside tipper 100b, 110b, 120b shown in comparative example 1,2,3 same
On spiral, the situation of (on same straight line) is compared, as present embodiment can be by upside tipper 82a and downside tipper 82b
It is configured in back-pressure contracting load surface, therefore, it is possible to reduce tilt angle theta 1, can suppresses by upside tipper 82a and downside
The reduction of the oil film pressure that tipper 82b brings, increases the fuel delivery to base bearing 42.
In addition, the oil of the internal diameter lower end supplied to base bearing 42 has due to the rotary motion of bent axle 41 and the viscosity of oil
The peripheral speed of corresponding 41 periphery of bent axle and the rotating speed that produces, so as to flowing in base bearing 42.After flowing, downside tipper is reached
The speed that the oil of 82b is produced using the gradient of corresponding downside tipper 82b is in the tipper 82b of downside, the tipper 82a of upside
Interior flowing, so as to the whole region to base bearing 42 carries out fuel feeding.In addition, as described above, by the segmentation located at base bearing 42
81 store oil of groove, can roll the lower end fuel feeding of skewed slot 82a upwards from the optional position of the inner circumferential tour of base bearing 42.And
And, such as shown in Fig. 5 (b), by the lower end 82a1 of upside tipper 82a located at the upper end 82b1 than downside tipper 82b more by song
The upstream side of the direction of rotation R1 (flow direction of oil) of axle 41, so as to the upper end 82b1 from downside tipper 82b reaches segmentation
The oil of groove 81 combines the direction of rotation R1 of bent axle 41, it can be ensured that the path length flowed in slot segmentation 81, it is possible to increase main shaft
Hold 42 cooling effect.
According to the motor compressor 1 of the first embodiment for so constituting, it is configured to possess slot segmentation 81, upside tipper
82a and downside tipper 82b, and from axial G overlook when, upside tipper 82a and downside tipper 82b is overlapped.So as to energy
Confession oiliness and lubricity to base bearing 42 is enough improved, it is possible to increase performance and reliability.Additionally, in the present embodiment, make
Although list base bearing 42 for bearing to be illustrated, but in supplementary bearing 44 similarly, by arrange tipper, oil from
The upper end of supplementary bearing 44 is flowed in tipper towards lower end, can carry out fuel feeding.In addition, in the case of supplementary bearing 44, root
According to the structure of motor compressor 1, supplementary bearing 44 integrally immerses the oil storage tank 23a of 2 bottom of hermetic container all the time, so without the need for inclining
The positive fuel feeding that groove is carried out.Accordingly it is also possible to be not provided with into tipper, and oil groove is arranged to the straight line parallel with axial G
Type.
In addition, in the first embodiment, relative to the compressive load of compression mechanical part 4, upside tipper 82a and downside
Tipper 82b is located at back-pressure contracting load surface (with reference to Fig. 5 (b)).Thereby, it is possible to prevent bent axle 41 and the metal of base bearing 42 from connecing
Touch, the reduction of slippage loss can be realized.
(second embodiment)
Fig. 9 represents the base bearing of second embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.Additionally,
For with first embodiment identical structure, mark identical symbol the repetitive description thereof will be omitted (for following embodiment party
Formula is similarly).In addition, illustrate only base bearing 42A in fig .9, for other structures, identical with first embodiment (right
In following embodiment similarly).
As shown in Fig. 9 (a), base bearing 42A possesses in the slot segmentation 81c that splits up and down of axial G, located at slot segmentation 81c
Upside upside tipper 82a and the downside tipper 82b located at the downside of slot segmentation 81c.In addition, base bearing 42A
Be formed as than upside tipper by the sectional area A1 (with reference to Fig. 9 (a)) of during plane cutting perpendicular to axial G, slot segmentation 81
The sectional area A3 (with reference to Fig. 9 (a)) of the sectional area A2 (with reference to Fig. 9 (a)) and downside tipper 82b of 82a is big.Sectional area A1 is referred to
The sectional area in the gap of the annular formed between base bearing 42 and bent axle 41.Sectional area A2, A3 are referred in 42 and of base bearing
The sectional area in the gap of the spill formed between bent axle 41.In addition, as shown in Fig. 9 (b), upside tipper 82a and downside incline
Groove 82b is same with first embodiment, when overlooking from axial G, is formed as overlapped.
According to the second embodiment for so constituting, the oil for reaching slot segmentation 81c from downside tipper 82b is once stored in
In slot segmentation 81, it is more effectively carried out cooling down therefore, it is possible to pass through the oil of slot segmentation 81c, it is possible to increase to the confession of base bearing 42A
Oiliness and lubricity, it is possible to increase performance and reliability.
(the 3rd embodiment)
Figure 10 represents the base bearing of the 3rd embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
As shown in Figure 10 (a), base bearing 42B is configured to, the groove depth score of upside tipper 82c and downside tipper 82d
The groove depth for cutting groove 81 is deeper, and a part of a part of upside tipper 82c and downside tipper 82d is located at segmentation respectively
In groove 81 (upside tipper 82c and downside tipper 82d enter into the midway of slot segmentation 81).
That is, as shown in Figure 10 (b), the lower end 82c1 of upside tipper 82c extends to the upper portion weight with slot segmentation 81
Folded position, the upper end 82d1 of downside tipper 82d extend to the position Chong Die with the lower portion of slot segmentation 81.In addition, logical
Cross and the groove depth of upside tipper 82c and downside tipper 82d is formed as more deeper than the groove depth of slot segmentation 81, can be in slot segmentation
81 form upside tipper 82c and downside tipper 82d.
According to the 3rd embodiment for so constituting, due to being able to ensure that oil is flowed from downside tipper 82d to slot segmentation 81
The opening (outlet) of stream when going out is broad, oil is liable to flow out to slot segmentation 81, further, since be able to ensure that oil from point
Opening (entrance) broadness that groove 81 rolls stream when skewed slot 82c is flowed into upwards is cut, therefore makes oil flow easily into upside tipper
82c.Thus, oil easily flows such that it is able to be more effectively carried out cooling down, it is possible to increase to the confession oiliness and lubrication of base bearing 42
Property, it is possible to increase performance and reliability.
(the 4th embodiment)
Figure 11 represents the base bearing of the 4th embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
As shown in Figure 11 (a), base bearing 42C is configured to, upside tipper 82e, downside tipper 82f and slot segmentation
The surface roughness of 81d is bigger than the surface roughness of inner peripheral sliding surface 42t (not forming the face of groove).Additionally, in Figure 11 (a), (b)
In, add some points to represent that surface roughness is bigger.
As shown in Figure 11 (b), each angle of inclination and first embodiment of upside tipper 82e and downside tipper 82f
Identical, in addition, upside tipper 82e and downside tipper 82f are formed as, all overlap when axially overlooking.
According to the 4th embodiment for so constituting, slot segmentation 81d, upside tipper 82e and downside tipper 82f's
Surface area ratio does not carry out the situation increase of rough surface, therefore, it is possible to be more effectively carried out cooling down by oil, it is possible to increase to
The confession oiliness of base bearing 42 and lubricity, it is possible to increase performance and reliability.
(the 5th embodiment)
Figure 12 represents the base bearing of the 5th embodiment, (a) is longitudinal sectional view, (b) is the expanded view of inner peripheral surface.
As shown in Figure 12 (a), base bearing 42D has slot segmentation 81e, the 81f (at least one that splits up and down in axial G
Slot segmentation) and relative to slot segmentation 81e, 81f be located at axial direction G upper and lower tipper 82g, 82h, 82i.In addition, tipper
82g, 82h, 82i are formed as inclining relative to axial G.
As shown in Figure 12 (b), the upper end 82g1 of tipper 82g is connected with the upper end of base bearing 42D, lower end 82g2 and segmentation
Groove 81e is connected.The upper end 82h1 of tipper 82h is connected with slot segmentation 81e, and lower end 82h2 is connected with slot segmentation 81f.Tipper
The upper end 82i1 of 82i is connected with the upper end of base bearing 42D, and lower end 82g2 is connected with slot segmentation 81e.
In addition, as shown in Figure 12 (b), tipper 82g, tipper 82h and tipper 82i are formed as bowing from axial G
Apparent time is mutually all overlapped.
In the 5th embodiment for so constituting, possess in the upper of axial G in inner peripheral sliding surface 42t of base bearing 42D
Slot segmentation 81e, 81f of lower segmentation and slot segmentation 81e, 81f upper and lower relative to axial G incline tipper 82g, 82h,
82i, and each tipper 82g, 82h, 82i be configured to, when the axial G from base bearing 42 is overlooked, all overlap.Accordingly, with upper
Roll skewed slot 100a, 110a, 120a and downside tipper 100b, 110b, 120b are located at (on same straight line) on same spiral
Situation compares (with reference to Fig. 6 to Fig. 8), can reduce the tilt angle theta 2 of tipper 82g, 82h, 82i than first embodiment.Cause
This, can be such that the fuel delivery to base bearing 42 further increases, and because possessing slot segmentation 81e, 81f, it is possible to effectively
Carry out the cooling of base bearing 42.So as to, in base bearing 42, supply oiliness by effectively carrying out the cooling of oil and improve
And lubricity, it is possible to increase the performance and reliability of motor compressor.
In addition, in the 5th embodiment, as in back-pressure contracting load surface, therefore tipper 82g, 82h, 82i are configured at
The reduction of the oil film pressure of tipper 82g, 82h, 82i can be suppressed, it is possible to increase the performance and reliability of motor compressor.
Additionally, in the 5th embodiment, although enumerate possess two slot segmentations 81e, 81f and three tipper 82g,
82h, 82i are illustrating, but can also possess the slot segmentation of more than three and the tipper of more than four.
Additionally, the present invention is not limited to above-mentioned embodiment, which includes various modifications example.For example, above-mentioned embodiment party
Formula for convenience of description the present invention and be illustrated in detail, and be not limited to possess the described all of structure for understanding.Separately
Outward, a part for the structure of certain embodiment can be replaced as the structure of other embodiment, in addition, it is also possible in certain enforcement
Add the structure of other embodiment in the structure of mode.In addition, for a part for the structure of each embodiment, can
Carry out adding, delete, replacing for other structures.
For example, in the above-described embodiment, hermetic type vertical revolving formula compressor is illustrated, and in base bearing
42 sides be provided with the oil groove between base bearing 42 and bent axle 41 (upside tipper 82a, 82c, 82e, downside tipper 82b, 82d,
82f, tipper 82g, 82h, 82i, slot segmentation 81,81c, 81d, 81e, 81f) situation.But, the present invention is not limited and this,
Can also be other structures, for example, non-hermetic type Rotary Compressor, scroll compressor, reciprocating compressor etc., in bent axle
41 sides are provided with the oil groove between base bearing 42 and bent axle 41.Alternatively, it is also possible to for equal in 42 side of base bearing and 41 side both sides of bent axle
The structure of the oil groove being provided between base bearing 42 and bent axle 41.
Claims (5)
1. a kind of motor compressor, it is characterised in that possess：
Motor；
Compression mechanical part, its have and carry out the bent axle of rotation driving using above-mentioned motor and support the bearing of above-mentioned bent axle, and
Sliding surface of the above-mentioned bent axle with above-mentioned bearing is lubricated using lubricating oil；And
Above-mentioned motor and compression mechanism section are received in incorporating section, its,
Above-mentioned bearing and/or above-mentioned bent axle have：
At least one slot segmentation, its above-mentioned sliding surface of segmentation up and down in the axial direction of above-mentioned bearing；And
Tipper, its relative to above-mentioned sliding surface above-mentioned slot segmentation be located at above-mentioned axial upper and lower, and relative to above-mentioned axial direction
Incline,
Each above-mentioned tipper is formed as, and when from above-mentioned axially vertical view, at least a portion is overlapped.
2. motor compressor according to claim 1, it is characterised in that
Compressive load of the above-mentioned tipper relative to compression mechanism section, is arranged at back-pressure contracting load surface.
3. motor compressor according to claim 1 and 2, it is characterised in that
The sectional area in above-mentioned axial plane of above-mentioned slot segmentation, more than above-mentioned tipper perpendicular to above-mentioned axial direction
Plane on sectional area.
4. the motor compressor according to any one of claims 1 to 3, it is characterised in that
The groove depth of above-mentioned tipper is more deeper than the groove depth of above-mentioned slot segmentation, and a part for above-mentioned tipper is located at above-mentioned segmentation
In groove.
5. the motor compressor according to any one of Claims 1 to 4, it is characterised in that
Surface roughness of the surface roughness of above-mentioned tipper and/or above-mentioned slot segmentation more than above-mentioned sliding surface.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015175273A JP6700691B2 (en) | 2015-09-07 | 2015-09-07 | Electric compressor |
| JP2015-175273 | 2015-09-07 |
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| Publication Number | Publication Date |
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| CN106499634A true CN106499634A (en) | 2017-03-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610590081.4A Pending CN106499634A (en) | 2015-09-07 | 2016-07-25 | Motor compressor |
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| JP (1) | JP6700691B2 (en) |
| CN (1) | CN106499634A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2020037887A (en) * | 2018-09-03 | 2020-03-12 | 日立ジョンソンコントロールズ空調株式会社 | Hermetic electric compressor |
| CN112145419B (en) * | 2019-06-28 | 2021-06-15 | 安徽美芝精密制造有限公司 | Pump body subassembly, compressor and air conditioner |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0447191A (en) * | 1990-06-14 | 1992-02-17 | Matsushita Electric Ind Co Ltd | Closed type rotary compressor |
| JP2007270818A (en) * | 2005-06-29 | 2007-10-18 | Matsushita Electric Ind Co Ltd | Fluid machinery and refrigerating cycle apparatus |
| CN201209560Y (en) * | 2007-11-13 | 2009-03-18 | 上海日立电器有限公司 | Rolling rotor type air-conditioned compressor with furcation oil groove |
| JP2010185342A (en) * | 2009-02-12 | 2010-08-26 | Panasonic Corp | Rotary motor-driven compressor |
| JP2010255448A (en) * | 2009-04-22 | 2010-11-11 | Panasonic Corp | Rotary compressor |
| JP2010255449A (en) * | 2009-04-22 | 2010-11-11 | Panasonic Corp | Rotary compressor |
| CN203856721U (en) * | 2013-04-16 | 2014-10-01 | 三菱电机株式会社 | Rotary type closed compressor |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5374171A (en) * | 1994-04-11 | 1994-12-20 | Tecumseh Products Company | Rotary compressor thrust washer |
| US5884727A (en) * | 1996-07-01 | 1999-03-23 | Samsung Electronics Co., Ltd. | Hermetic compressor with start-up lubrication |
| JP3459545B2 (en) * | 1997-09-01 | 2003-10-20 | 三洋電機株式会社 | Oil supply device for compressor |
| JP4617656B2 (en) * | 2003-10-14 | 2011-01-26 | パナソニック株式会社 | Hermetic compressor |
| JP5685742B2 (en) * | 2012-10-23 | 2015-03-18 | パナソニックＩｐマネジメント株式会社 | Rotary compressor |
| JP6273729B2 (en) * | 2013-09-12 | 2018-02-07 | ダイキン工業株式会社 | Rotary compressor |
-
2015
- 2015-09-07 JP JP2015175273A patent/JP6700691B2/en active Active
-
2016
- 2016-07-25 CN CN201610590081.4A patent/CN106499634A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0447191A (en) * | 1990-06-14 | 1992-02-17 | Matsushita Electric Ind Co Ltd | Closed type rotary compressor |
| JP2007270818A (en) * | 2005-06-29 | 2007-10-18 | Matsushita Electric Ind Co Ltd | Fluid machinery and refrigerating cycle apparatus |
| CN201209560Y (en) * | 2007-11-13 | 2009-03-18 | 上海日立电器有限公司 | Rolling rotor type air-conditioned compressor with furcation oil groove |
| JP2010185342A (en) * | 2009-02-12 | 2010-08-26 | Panasonic Corp | Rotary motor-driven compressor |
| JP2010255448A (en) * | 2009-04-22 | 2010-11-11 | Panasonic Corp | Rotary compressor |
| JP2010255449A (en) * | 2009-04-22 | 2010-11-11 | Panasonic Corp | Rotary compressor |
| CN203856721U (en) * | 2013-04-16 | 2014-10-01 | 三菱电机株式会社 | Rotary type closed compressor |
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| Publication number | Publication date |
|---|---|
| JP2017053221A (en) | 2017-03-16 |
| JP6700691B2 (en) | 2020-05-27 |
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Effective date of registration: 20180614 Address after: Tokyo, Japan, Japan Applicant after: Hitachi Johnson Controls Air Conditioning Co., Ltd. Address before: Hongkong, China Applicant before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. |
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Application publication date: 20170315 |