CN106351833B - Compressor - Google Patents
Compressor Download PDFInfo
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- CN106351833B CN106351833B CN201610546572.9A CN201610546572A CN106351833B CN 106351833 B CN106351833 B CN 106351833B CN 201610546572 A CN201610546572 A CN 201610546572A CN 106351833 B CN106351833 B CN 106351833B
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- region
- groove portion
- opposite side
- flange part
- main shaft
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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
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
Abstract
The present invention relates to a kind of compressors, have in closed container：Compression mechanical part carries out compression to refrigerant and the refrigerant is discharged from outlet；And motor part, compression mechanical part is driven via main shaft, compression mechanical part includes：The cylinder body of hollow cylinder shape；And upper bearing (metal) and lower bearing, they are respectively arranged at the axial both ends of cylinder body and are supported to main shaft, upper bearing (metal) and lower bearing have the flange part for closing off the upper and lower opening face in the axial direction of cylinder body, the groove portion for having outlet is formed in flange part, in flange part, thickness across main shaft positioned at the region of the opposite side of groove portion is gradually changed with far from main shaft, about the axial of cylinder body, the formation of flange part has the size of the cross sectional moment of inertia in the region of that side of groove portion, with across main shaft and positioned at groove portion opposite side region cross sectional moment of inertia it is equal in magnitude.
Description
Technical field
The present invention relates to closed rotary compressors.
Background technology
In general compressor, in order to reduce the remaining compression refrigeration because not being discharged from the outlet of compression refrigerant
Agent flows backwards generated recompression loss to discharge chambe, and the thickness for the discharge valve seat for being set to bearing is thinned.For the row of being thinned
Go out the thickness of valve seat and slot is set in bearing flange portion.Moment of flexure near the slot is small, therefore, fastens bearing using screw etc.
When being linked to cylinder body, bearing flange portion deforms and makes the face flexure of its discharge chambe side.In addition, the face of discharge chambe side is also because of compression
Internal pressure in machine operation process and further bend.Gap between the face and piston of the compressor side in bearing flange portion as a result,
Increase.As a result, leakage loss increases in discharge chambe, compression efficiency reduces.
It, sometimes will be for generating and the discharge because being set to bearing flange as the method for the deformation for inhibiting bearing flange portion
Valve seat and the grooving of the equivalent moment of flexure of moment of flexure that generates is disposed in bearing flange (patent document 1).The grooving, which is matched, to be set as so that axis
Boss (boss) is held to be located between discharge valve seat and the grooving.In addition, it is also known that following structure：By keeping the flange part of bearing whole
Body thickeies and improves rigidity, thus inhibits the deformation (patent document 2) of bearing.
Patent document 1：Japanese Unexamined Patent Publication 2009-236075 bulletins
Patent document 2：Japanese Unexamined Patent Publication 2007-56860 bulletins
However, in the case where being provided with grooving as described in Patent Document 1, although the moment of flexure in bearing flange portion can be across
Bearing boss and become equivalent, but since the wall thickness of grooving is small, can not prevent from leading to grooving portion because of compressor internal pressure
Degree of flexibility increases, to there are problems that leakage loss increase.
In addition, as described in Patent Document 2 in bearing flange portion Integral upset is improved rigid method, in addition to
Restriction in terms of compressor construction becomes except project, there is a problem in that：Make axis because only having slot to be formed due to part is bent
Holding the gap between the discharge chambe side surface of flange part and the axial end portion of cylinder body becomes uneven, increases so as to cause leakage loss
Greatly.
Invention content
The purpose of the present invention is to provide a kind of recompression loss and leakage loss is small and compressor that compression efficiency is high.
The compressor of the present invention has in closed container：Compression mechanical part, to the refrigerant that is sucked from suction inlet into
Simultaneously the refrigerant is discharged from outlet for row compression；And motor part, compression mechanism section is carried out via main shaft
Driving, the compressor are characterized in that compression mechanism section includes：The cylinder body of hollow cylinder shape；And upper bearing (metal) is under
Bearing, they are respectively arranged at the axial both ends of above-mentioned cylinder body and are supported to above-mentioned main shaft, and above-mentioned upper bearing (metal) has will
The upper crown of roll edge of the opening face closure of axial one end of above-mentioned cylinder body, above-mentioned lower bearing has the axial direction of above-mentioned cylinder body is another
The lower axle flange part of the opening face closure at end, at least one party's in above-mentioned upper crown of roll edge and above-mentioned lower axle flange part is convex
Edge is formed with the groove portion for having above-mentioned outlet, phase in above-mentioned flange part, across above-mentioned main shaft and positioned at above-mentioned groove portion
The thickness in the region tossed about is gradually changed with far from above-mentioned main shaft.
It is preferably located at the region of the opposite side of the groove portion, is when to the vertical view of the flange part by from the master
Axis centrally through two regions marking off of line of demarcation in, relative to that side for being formed with the groove portion region across
The line of demarcation and positioned at opposite side region.
The thickness of the flange part in the region of the opposite side of the groove portion is preferably located at far from the main shaft and
It is thinning.
It is being preferably located at the flange part in the region of the opposite side of the groove portion, the compression mechanical part opposite
The face of side tilts.
Preferably, flange part fastening is linked to the end of the cylinder body using fixed component, is formed with the slot
Region of the number of the fixed component in the region of that side in portion than the opposite side across the main shaft and positioned at the region
The number of the interior fixed component is more.
The thickness of the flange part in the region of the opposite side of the groove portion is preferably located at far from the line of demarcation
And it thickens.
It is being preferably located at the flange part in the region of the opposite side of the groove portion, the compression mechanical part opposite
The face of side tilts.
Preferably, flange part fastening is linked to the end of the cylinder body using fixed component, is formed with the slot
Region of the number of the fixed component in the region of that side in portion than the opposite side across the main shaft and positioned at the region
The number of the interior fixed component is few.
Preferably, the formation about the axial direction of above-mentioned cylinder body, above-mentioned flange part has the region of that side of above-mentioned groove portion
The size of cross sectional moment of inertia, the size with the cross sectional moment of inertia in the region of the opposite side across above-mentioned main shaft and positioned at above-mentioned groove portion
It is equal.
Preferably, from the main shaft by and with the line of demarcation vertically intersect cross on line, the described flange
The formation in portion has the sectional area in the region of that side of the groove portion, the area with the opposite side across the main shaft and positioned at the region
The sectional area in domain is equal.
It is being preferably located at the flange part in the region of the opposite side of the groove portion, the compression mechanical part opposite
The face of side is the inclined surface without step difference.
It is being preferably located at the flange part in the region of the opposite side of the groove portion, the compression mechanical part opposite
The face of side so that the amount bent to the compression mechanical part side of the groove portion side with described in opposite side to the groove portion
The identical mode of amount of compression mechanical part side flexure tilts.
Preferably, the face of the compression mechanical part side of the flange part is single plane.
The compressor of the present invention can reduce recompression loss and leakage loss and improve compression efficiency.
Description of the drawings
Fig. 1 is the longitudinal section view for the compressor for showing embodiments of the present invention 1.
Fig. 2 is the sectional elevation for the compressor for showing embodiments of the present invention 1.
Fig. 3 is the side view of the bearing of Fig. 1.
Fig. 4 is the vertical view of the bearing of Fig. 1.
Fig. 5 is the side view of the variation for the bearing for showing Fig. 1.
Fig. 6 is the vertical view of the variation for the bearing for showing Fig. 1.
Fig. 7 is the schematic diagram of the longitudinal section of the upper bearing (metal) of the compressor of embodiments of the present invention 2.
Fig. 8 is the schematic diagram of the longitudinal section for the model that upper bearing (metal) flange part is assumed to cantilever beam.
Reference sign：
1 ... closed container；2 ... motor parts；3 ... compression mechanical parts；4 ... main shafts；5 ... eccentric shafts；6 ... cylinder bodies；On 7 ...
Bearing；7a ... upper bearing (metal) flange parts；7a1 ... discharge chambes side surface；7a2 ... boss side surface；7b ... upper bearing (metal) boss portions；8…
Lower bearing；8a ... lower bearing flange parts；8b ... lower bearing boss portions；9 ... pistons；10 ... blade grooves；11 ... blades；12 ... springs
Component；13 ... discharge chambes；14 ... suction inlets；15 ... outlets；15a ... dump valves；16 ... groove portions；17 ... fixed components；17a~
17e ... fastens linking part；100 ... compressors.
Specific implementation mode
Embodiment 1.
Fig. 1 is the longitudinal section view for the compressor 100 for showing present embodiment.Fig. 2 is the sectional elevation of compressor 100.Pressure
Contracting machine 100 has motor part 2 and compression mechanical part 3 in closed container 1.Motor part 2 transmits rotor via main shaft 4
Thus the rotary force of 2a drives compression mechanical part 3.In compression mechanical part 3, discharge chambe 13 be configured to include：It is hollow
The cylinder body 6 of cylindrical shape；Upper bearing (metal) 7 is set to the upper axial end of cylinder body 6；And lower bearing 8, it is set to lower end.Main shaft
4 upside is supported on upper bearing (metal) boss portion 7b in a way freely spinning way, and the downside of main shaft 4 is supported in a way freely spinning way
Lower bearing boss portion 8b.It is provided in discharge chambe 13：Cricoid piston 9 in a manner of sliding freely and is fixed on main shaft 4
Eccentric shaft 5 it is chimeric and be eccentrically rotated；And blade 11, be accommodated in along cylinder body 6 the blade groove 10 radially extended and
Piston 9 is pressed on by spring members 12.Low pressure is divided by the blade 11 for being pressed on piston 9 by spring members 12 in discharge chambe 13
Space and high-pressure space.In the action of compressor 100, the rotary force of motor part 2 is transferred to piston 9 via main shaft 4.It is living
Plug 9 is eccentrically rotated in discharge chambe 13, to be sucked from the suction inlet 14 formed in the side of cylinder body 6 into discharge chambe 13
The refrigerant of low pressure makes the volume change of low-voltage space and high-pressure space in discharge chambe 13, one on one side by the rotation of piston 9
While being compressed to refrigerant.Be compressed to high pressure refrigerant jack up upward by the flange part of upper bearing (metal) 7 (hereinafter, claim
For upper bearing (metal) flange part 7a) formed outlet 15 cover dump valve 15a and discharged to outside discharge chambe 13.
Compression mechanical part 3 is provided with bilevel discharge chambe 13.The pressure of the structure and upper layer of the discharge chambe 13 of lower layer
The structure of contracting room 13 is identical.It is identical as upper bearing (metal) flange part 7a, in flange part (the hereinafter referred to as lower bearing flange part of lower bearing 8
The dump valve for 8a) being also formed with outlet and covering the outlet, compressed refrigerant jack up dump valve upward
And it is discharged to outside discharge chambe 13.In addition, Fig. 1 is provided with the example of the case where bilevel discharge chambe 13, but can also
Be formed as the structure for the discharge chambe 13 for being provided only with either one.In addition, be omitted in Fig. 1 closed container 1 top and under
The diagram in portion, but closed container 1 is the container of airtight construction.It is stored with mainly in the bottom of closed container 1 to carrying out sliding fortune
Dynamic piston 9 implements the refrigerator oil (not shown) of lubrication.As refrigerant, HFO-1234yf, HFO- can be used for example
Mix refrigerant, the propane of 1123 equal unitary systems cryogens or the HFC refrigerants such as these above-mentioned unitary system cryogens and R32
(R290) natural refrigerants such as hydrocarbon refrigerants or carbon dioxide such as.
Fig. 3 is the side view of the upper bearing (metal) 7 of compressor 100.Fig. 4 is the vertical view of the upper bearing (metal) 7 of compressor 100.Upper axis
Hold the upper end that flange part 7a is linked to cylinder body 6 (Fig. 1) by the fixed components such as screw 17 by fastening.Fastening linking part 17a~
17e is circumferentially disposed along cylinder body 6.In addition, fastening linking part 17a~17e is along the outer of the rounded upper bearing (metal) flange part 7a of vertical view
Week setting.The failure because of caused by the thermal expansion of the piston 9 rotated when compressor 100 operates in order to prevent, it is convex in upper bearing (metal)
Constant gap is provided between edge 7a and piston 9.
The face 7a1 (hereinafter referred to as discharge chambe side surface 7a1) of 3 side of compression mechanical part of upper bearing (metal) flange part 7a is not by having
There is the single plane of inclined surface to constitute, which covers the axis of cylinder body 6 (Fig. 1) opening face to the upper side.Separately
On the one hand, the face 7a2 of upper bearing (metal) flange part 7a, compression mechanical part 3 opposite side (sides upper bearing (metal) boss portion 7b) is (hereinafter, claim
For boss side surface 7a2) a part tilt.Specifically, upper bearing (metal) flange part 7a, across main shaft 4 be located at groove portion 16
The thickness in the region of opposite side is gradually changed with far from main shaft 4.In addition, specifically, when to the vertical view of upper bearing (metal) 7 by
From main shaft 4 centrally through two regions marking off (hereinafter, for convenience of description, referred to as line of demarcation A-A) line A-A in
, relative to that side for being formed with groove portion 16 region D1 (hereinafter referred to as slot side region D1) be located at across line of demarcation A-A it is opposite
The thickness of the upper bearing (metal) flange part 7a of the region D2 (hereinafter referred to as opposite side region D2) of side, with far from line of demarcation A-A and by
Gradual change is thin.Slot side region D1 and opposite side region D2 is semicircle area adjacent to each other respectively using line of demarcation A-A as boundary
Domain.
Boss of the boss side surface 7a2 relative to slot side region D1 in upper bearing (metal) flange part 7a, opposite side region D2
Side surface 7a2 is tilted.As shown in figure 4, slot side region D1 can be set as and groove portion 16 with the line of demarcation A-A of opposite side region D2
Length direction center line B-B it is parallel (hereinafter, for convenience of description, referred to as groove center line B-B).Hereinafter, for the ease of saying
It is bright, it will be known as crossing line C-C centrally through and with line C-C that line of demarcation A-A vertically intersects from main shaft 4.Upper bearing (metal) flange
The thickness H1 of edge C1s of the thickness H2 than slot side region D1 of the edge C2 for crossing the opposite side region D2 on line C-C of portion 7a
It is thin.In order not to make the rigidity of the upper bearing (metal) flange part 7a of opposite side region D2 excessively reduce, preferred thickness H2 is the 1/2 of thickness H1
More than.
Relative to cylinder body 6, upper bearing (metal) flange part 7a slot side region D1 fastening binding strength and opposite side region D2
Fastening binding strength it is equal or roughly equal in the case of, play following effect.Since the thickness H3 of groove portion 16 is than slot lateral areas
The thickness H1 of the upper bearing (metal) flange part 7a of domain D1 is thin, so groove portion 16 is easy to bend to the direction of 13 side of discharge chambe, power is making
Upper bearing (metal) boss portion 7b plays a role on the inclined direction in the sides slot side region D1.On the other hand, due to opposite side region D2's
The thickness H2 of upper bearing (metal) flange part 7a is gradually thinning with separate line of demarcation A-A, so power is making upper bearing (metal) boss portion 7b
It plays a role on the inclined direction in the sides opposite side region D2.According to above structure, due to the bending towards the sides slot side region D1
Power is cancelled out each other with the bending force towards the sides opposite side region D2, so the discharge because caused by being provided with groove portion 16 can be prevented
The case where upper bearing (metal) flange part 7a near groove portion 16 is bent to 3 side of compression mechanical part.Therefore, discharge chambe side surface 7a1 and work
Gap between plug 9 becomes uniform, so as to reduce leakage loss.
The boss side surface 7a2 of upper bearing (metal) flange part 7a is preferably so that axial G about cylinder body 6, slot side region D1
The size of cross sectional moment of inertia, angle F identical with the size of the cross sectional moment of inertia of opposite side region D2 and tilt.Slot side region
The size of D1 and the opposite respective cross sectional moment of inertias of side region D2 by fastening linking part 17a~17e respective positions relationship, this
A little fastening linking parts are determined with the parameters such as the position relationship of groove portion 16 and the size of fastening binding strength.Upper bearing (metal) flange part 7a
The angle of inclination F of boss side surface 7a2 of opposite side region D2 can also be determined by the simulation based on above-mentioned parameter, energy
It is enough simply to consider design in the following manner.
As shown in Figure 4, it is believed that the number of fastening linking part 17a~17c in slot side region D1 is than opposite lateral areas
In the case of more than the number of fastening linking part 17d and 17e in the D2 of domain, the discharge chambe side surface 7a1 of slot side region D1 is easy
It is bent to 13 side of discharge chambe.Under the above structure, as shown in figure 4, by making upper bearing (metal) flange part 7a, opposite lateral areas
The thickness of domain D2 is thinning with separate line of demarcation A-A, enables to the slot side region D1 about axial G and opposite side region
The respective cross sectional moment of inertias of D2 are equal and prevent the flexure of discharge chambe side surface 7a1.Especially in fastening linking part 17a~17e
In the case of respective fastening connection structure or fastening binding strength are identical, prevent the effect of flexure larger.
Fig. 5 is the side view for the variation for showing upper bearing (metal) 7.Fig. 6 is the vertical view for the variation for showing upper bearing (metal) 7.
In the upper bearing (metal) 7 of Fig. 5 and Fig. 6, the inclined direction and fastening linking part of the opposite side region D2 of upper bearing (metal) flange part 7a
The configuration of 17a~17e is different from the upper bearing (metal) 7 of Fig. 3 and Fig. 4.Since other structures are identical as the above embodiment, so saving
Slightly its explanation.
As shown in fig. 6, the number of fastening the linking part 17a and 17b in slot side region D1 are than in opposite side region D2
Fastening linking part 17c~17e number it is few in the case of, the discharge chambe side surface 7a1 of slot side region D1 can be to discharge chambe
13 opposite side flexure.Under the above structure, as shown in fig. 6, by making upper bearing (metal) flange part 7a, opposite side region
The thickness of D2 enables to about axial G, slot side region D1 and opposite side region with thickeing far from line of demarcation A-A
The respective cross sectional moment of inertias of D2 are equal and prevent the flexure of discharge chambe side surface 7a1.Especially in fastening linking part 17a~17e
In the case of respective fastening connection structure or fastening binding strength are identical, prevent the effect of flexure larger.
It, can be simple in order to keep cross sectional moment of inertia equal in the structure and Fig. 5 of Fig. 3 and Fig. 4 and the structure of Fig. 6
Ground is designed based on the size of sectional area.If that is, it is contemplated that the slot side of upper bearing (metal) flange part 7a crossed on line C-C
Region D1 and the opposite respective sectional areas of side region D2 are equal, then about axial G, slot side region D1 and opposite side region
The respective cross sectional moment of inertias of D2 are almost equal.In order to make to cross slot side region D1 on line C-C and opposite side region D2 respectively
Sectional area it is equal, so that the boss side surface 7a2 of upper bearing (metal) flange part 7a is tilted, so that about axial G, slot side
Region D1 and the opposite respective cross sectional moment of inertias of side region D2 are equal and prevent the flexure of discharge chambe side surface 7a1.
As shown in Fig. 3 and Fig. 4 and Fig. 5 and Fig. 6, the boss side surface of the opposite side region D2 of upper bearing (metal) flange part 7a
7a2 is preferably the inclined surface without step difference.According to above structure, do not produced in the upper bearing (metal) flange part 7a of opposite side region D2
The inflection point of raw stress, so as to inhibit the flexure of the sides opposite side region D2, and is easy to be formed as and the sides slot side region D1
Moment of flexure is equivalent.In addition, though the boss side surface 7a2 of the opposite side region D2 of upper bearing (metal) flange part 7a is tilted, but discharge chambe side
Surface 7a1 is not tilted, therefore the gap between discharge chambe side surface 7a1 and piston 9 can be made to minimize, and is let out to be difficult to generate
Leakage loss is lost.In this way, compressor 1 according to the present embodiment, can not only reduce recompression loss, but also can reduce leakage
Loss, so as to improve compression efficiency.
The above embodiment is created as making the case where boss side surface 7a2 of upper bearing (metal) flange part 7a inclined structures
Example can also be formed as being allowed to inclined in the same manner as the above embodiment for the boss side surface of lower bearing flange part 8a
Structure.In this case identical effect is played also by identical effect.
Embodiment 2.
Fig. 7 is the upper bearing (metal) 7 when being shown in solid lines the longitudinal section of the upper bearing (metal) 7 when not bending and being shown in broken lines flexure
Longitudinal section schematic diagram.In the compressor 100 of present embodiment, so that the maximum deflection of the upper bearing (metal) 7 of 16 side of groove portion
C, the mode equal with the maximum deflection d of upper bearing (metal) 7 of opposite side of groove portion 16 is in across main shaft 4, determines upper bearing (metal)
The thickness of flange part 7a.Maximum deflection c is the inner peripheral portion 7a3 of the discharge chambe side surface 7a1 of 16 side of groove portion when not bending
Vertical direction distance between the position of the inner peripheral portion 7a3 of the discharge chambe side surface 7a1 of 16 side of groove portion when position and flexure.
Maximum deflection d be the inner peripheral portion 7a3 of the discharge chambe side surface 7a1 of the opposite side of the groove portion 16 when not bending position, with scratch
Vertical direction distance between the position of the inner peripheral portion 7a3 of the discharge chambe side surface 7a1 of the opposite side of groove portion 16 when bent.Upper axis
The boss side surface 7a2 for holding 16 side of groove portion of flange part 7a tilts as so that maximum deflection c is identical as maximum deflection d.
Fig. 8 is that upper bearing (metal) flange part 7a is assumed to using the peripheral part 7a4 of discharge chambe side surface 7a1 as the general of fixed point
Cantilever beam model longitudinal section schematic diagram.In the model, if the unilateral cross sectional moment of inertia of upper bearing (metal) 7 is set as I,
Vertical coefficient of elasticity is set as E, the power that upper bearing (metal) flange part 7a is fixed on cylinder body 6 by fixed component 17 is set as P, by fixed component 17
The horizontal distance of peripheral part 7a4 of position to discharge chambe side surface 7a1 be set as a, by the position of fixed component 17 to discharge chambe
The horizontal distance of the inner peripheral portion 7a3 of side surface 7a1 is set as b, then maximum deflection y is formed as following formula.
【Mathematical expression 1】
Deflection can be calculated using above-mentioned mathematical expression, such as can also be constructed calculating instrument using CAE etc. and be carried out
It calculates.If defining specific size and calculating deflection, the upper bearing (metal) flange part 7a of 16 side of groove portion can be realized
8.1 μm of deflection and groove portion 16 opposite side upper bearing (metal) flange part 7a 6.7 μm of deflection.In groove portion 16
In the case of the boss side surface 7a2 of opposite side is not inclined, that is, in the thickness and slot of the upper bearing (metal) flange part 7a of 16 side of groove portion
In the case of the thickness of the upper bearing (metal) flange part 7a of the opposite side in portion 16 is identical, the opposite to that side of deflection of 16 side of groove portion is scratched
The difference of song amount is larger.On the other hand, in the compressor of present embodiment 100, the boss side surface 7a2 of the opposite side of groove portion 16
It is angled such that the thickness of the edge C2 of the upper bearing (metal) flange part 7a of the opposite side of groove portion 16 is formed as the upper bearing (metal) of 16 side of groove portion
70% thickness of the thickness of the edge C1 of flange part 7a.In this case, the opposite side of groove portion 16 can be found out by calculating
Deflection be 8.3 μm.The difference of the deflection of 16 side of groove portion and the deflection of the opposite side of groove portion 16 is 0.2 μ (about 3%
Difference), deflection is almost consistent.Preferably allow for deflection to reach 1 μm or so, and preferably make deflection difference be in ± 10% with
It is interior.
In the compressor 100 of the present embodiment, so that the deflection and groove portion of the upper bearing (metal) flange part 7a of 16 side of groove portion
The identical mode of deflection of the upper bearing (metal) flange part 7a of 16 opposite side makes the boss side surface 7a2 of the opposite side of groove portion 16 incline
Tiltedly.According to above structure, equilibrium can be ensured in the opposite side of 16 side of groove portion and groove portion 16, as a result, it is possible to make discharge chambe
Gap between side surface 7a1 and piston 9 becomes uniform, so as to reduce leakage loss.
Claims (13)
1. a kind of compressor, has in closed container：Compression mechanical part presses the refrigerant sucked from suction inlet
It contracts and the refrigerant is discharged from outlet；And motor part, the compression mechanical part is driven via main shaft,
The compressor is characterized in that,
The compression mechanical part includes：The cylinder body of hollow cylinder shape；And upper bearing (metal) and lower bearing, they are respectively arranged at institute
It states the axial both ends of cylinder body and the main shaft is supported,
The upper bearing (metal) has the upper crown of roll edge of the opening face closure of axial one end of the cylinder body, and the lower bearing has
By the axial other end of the cylinder body opening face closure lower axle flange part,
The flange part of at least one party in the upper crown of roll edge and the lower axle flange part, which is formed with, has the discharge
The groove portion of mouth,
The thickness in the region of opposite side in the flange part, being located at the groove portion across the main shaft is with far from the master
Axis and gradually change.
2. compressor according to claim 1, which is characterized in that
Positioned at the region of the opposite side of the groove portion, be when to the vertical view of the flange part by from the main shaft centrally through
Two regions marking off of line of demarcation in, relative to that side for being formed with the groove portion region across the line of demarcation and
Positioned at the region of opposite side.
3. compressor according to claim 1 or 2, which is characterized in that
Thickness positioned at the flange part in the region of the opposite side of the groove portion is thinning with the separate main shaft.
4. compressor according to claim 3, which is characterized in that
Positioned at the region of the opposite side of the groove portion the flange part, the face of the opposite side of the compression mechanical part tilts.
5. compressor according to claim 3, which is characterized in that
Flange part fastening is linked to the end of the cylinder body using fixed component,
The number ratio for being formed with the fixed component in the region of that side of the groove portion is located at the area across the main shaft
The number of the fixed component in the region of the opposite side in domain is more.
6. compressor according to claim 2, which is characterized in that
Thickness positioned at the flange part in the region of the opposite side of the groove portion thickens with far from the line of demarcation.
7. compressor according to claim 6, which is characterized in that
Positioned at the region of the opposite side of the groove portion the flange part, the face of the opposite side of the compression mechanical part tilts.
8. compressor according to claim 6, which is characterized in that
Flange part fastening is linked to the end of the cylinder body using fixed component,
The number ratio for being formed with the fixed component in the region of that side of the groove portion is located at the area across the main shaft
The number of the fixed component in the region of the opposite side in domain is few.
9. compressor according to claim 1 or 2, which is characterized in that
The formation of axial, the described flange part about the cylinder body has the cross sectional moment of inertia in the region of that side of the groove portion
Size, with across the main shaft and positioned at the groove portion opposite side region cross sectional moment of inertia it is equal in magnitude.
10. compressor according to claim 2, which is characterized in that
From the main shaft by and with the formation for crossing on line, the described flange part that vertically intersects of the line of demarcation
State the region of that side of groove portion sectional area, with across the main shaft and positioned at the region opposite side region sectional area phase
Deng.
11. compressor according to claim 4, which is characterized in that
Positioned at the region of the opposite side of the groove portion the flange part, the face of the opposite side of the compression mechanical part be not have
There is the inclined surface of step difference.
12. compressor according to claim 4, which is characterized in that
Positioned at the region of the opposite side of the groove portion the flange part, the face of the opposite side of the compression mechanical part so that
Obtain the compression mechanical part of the amount bent to the compression mechanical part side of the groove portion side and the opposite side to the groove portion
The identical mode of amount of side flexure tilts.
13. compressor according to claim 1 or 2, which is characterized in that
The face of the compression mechanical part side of the flange part is single plane.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2015/069997 | 2015-07-13 | ||
| PCT/JP2015/069997 WO2017009917A1 (en) | 2015-07-13 | 2015-07-13 | Compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106351833A CN106351833A (en) | 2017-01-25 |
| CN106351833B true CN106351833B (en) | 2018-07-20 |
Family
ID=57757818
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610546572.9A Active CN106351833B (en) | 2015-07-13 | 2016-07-12 | Compressor |
| CN201620731694.0U Withdrawn - After Issue CN206000729U (en) | 2015-07-13 | 2016-07-12 | Compressor |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620731694.0U Withdrawn - After Issue CN206000729U (en) | 2015-07-13 | 2016-07-12 | Compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6418329B2 (en) |
| CN (2) | CN106351833B (en) |
| WO (1) | WO2017009917A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6418329B2 (en) * | 2015-07-13 | 2018-11-07 | 三菱電機株式会社 | Compressor |
| CN107091232B (en) * | 2017-06-30 | 2020-04-03 | 广东美芝制冷设备有限公司 | Cover seal and cover seal assembly for compressor and compressor |
| CN107100842B (en) * | 2017-06-30 | 2020-03-06 | 广东美芝制冷设备有限公司 | Compression mechanism of compressor and compressor with same |
| CN107091230B (en) * | 2017-06-30 | 2020-03-06 | 广东美芝制冷设备有限公司 | Compressor and refrigerating device with same |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007056860A (en) * | 2006-03-30 | 2007-03-08 | Sanyo Electric Co Ltd | Rotary compressor |
| JP4016625B2 (en) * | 2001-09-26 | 2007-12-05 | 松下電器産業株式会社 | Hermetic rotary compressor |
| JP2009236075A (en) * | 2008-03-28 | 2009-10-15 | Panasonic Corp | Rotary compressor |
| CN102472276A (en) * | 2009-08-10 | 2012-05-23 | Lg电子株式会社 | Compressor |
| CN206000729U (en) * | 2015-07-13 | 2017-03-08 | 三菱电机株式会社 | Compressor |
-
2015
- 2015-07-13 JP JP2017528025A patent/JP6418329B2/en not_active Expired - Fee Related
- 2015-07-13 WO PCT/JP2015/069997 patent/WO2017009917A1/en active Application Filing
-
2016
- 2016-07-12 CN CN201610546572.9A patent/CN106351833B/en active Active
- 2016-07-12 CN CN201620731694.0U patent/CN206000729U/en not_active Withdrawn - After Issue
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4016625B2 (en) * | 2001-09-26 | 2007-12-05 | 松下電器産業株式会社 | Hermetic rotary compressor |
| JP2007056860A (en) * | 2006-03-30 | 2007-03-08 | Sanyo Electric Co Ltd | Rotary compressor |
| JP2009236075A (en) * | 2008-03-28 | 2009-10-15 | Panasonic Corp | Rotary compressor |
| CN102472276A (en) * | 2009-08-10 | 2012-05-23 | Lg电子株式会社 | Compressor |
| CN206000729U (en) * | 2015-07-13 | 2017-03-08 | 三菱电机株式会社 | Compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2017009917A1 (en) | 2017-09-14 |
| CN106351833A (en) | 2017-01-25 |
| WO2017009917A1 (en) | 2017-01-19 |
| CN206000729U (en) | 2017-03-08 |
| JP6418329B2 (en) | 2018-11-07 |
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