CN206000729U - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- CN206000729U CN206000729U CN201620731694.0U CN201620731694U CN206000729U CN 206000729 U CN206000729 U CN 206000729U CN 201620731694 U CN201620731694 U CN 201620731694U CN 206000729 U CN206000729 U CN 206000729U
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- China
- Prior art keywords
- region
- flange part
- groove portion
- opposition side
- main shaft
- Prior art date
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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 utility model is related to a kind of compressor, and which possesses in closed container：Compression mechanical part, its are compressed to cold-producing medium and discharge the cold-producing medium from outlet；And motor part, which is driven to compression mechanical part via main shaft, and 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 main shaft are supported, 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 possessing outlet is formed with flange part, in flange part, the thickness in region of the opposition side of groove portion is located at across main shaft with gradually changing away from main shaft, axial direction with regard to 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, equal in magnitude with the cross sectional moment of inertia in the region of the opposition side for being located at groove portion across main shaft.
Description
Technical field
The utility model is related to closed rotary compressor.
Background technology
In general compressor, in order to reduce the compression refrigeration because not discharging and remaining from the outlet of compression refrigerant
Agent flows backwards produced recompression loss to discharge chambe, and the thickness that will be arranged at the discharge valve seat of bearing is thinning.For thinning row
Go out the thickness of valve seat and groove is set in bearing flange portion.Moment of flexure near the groove is little, therefore, is fastening bearing using screw etc.
When being linked to cylinder body, bearing flange portion deforms and the face of its discharge chambe side is bent.In addition, the face of discharge chambe side is also because of compression
Internal pressure in machine operation process and bend further.Thus, the gap between the face of the compressor side in bearing flange portion and piston
Increase.As a result, leakage loss is in the indoor increase of compression, compression efficiency reduces.
As the method for the deformation in suppression bearing flange portion, sometimes by for producing and the discharge because being arranged at bearing flange
Valve seat and the grooving of moment of flexure of moment of flexure equivalent that produces is disposed in bearing flange (patent document 1).The grooving is arranged as causing axle
Hold boss (boss) to be located between discharge valve seat and the grooving.In addition, it is also known that following structure：Whole by the flange part for making bearing
Body thickeies and improves rigidity, thus suppresses the deformation (patent document 2) of bearing.
Patent document 1：Japanese Unexamined Patent Publication 2009-236075 publication
Patent document 2：Japanese Unexamined Patent Publication 2007-56860 publication
However, in the case of grooving is provided with as described in Patent Document 1, although the moment of flexure in bearing flange portion can be across
Bearing boss and become equivalent, but as the wall thickness of grooving is little, therefore cannot prevent from causing grooving portion because of compressor internal pressure
Degree of flexibility increases, so as to there is leakage loss increase.
In addition, as described in Patent Document 2 by improving bearing flange portion Integral upset in rigid method, except
Restriction in terms of compressor construction becomes outside problem, there is a problem in that：Axle is caused because only having the flexure of groove forming part
Holding the gap between the discharge chambe side surface of flange part and the axial end portion of cylinder body becomes uneven, so as to cause leakage loss to increase
Greatly.
Utility model content
The purpose of this utility model is to provide the pressure that a kind of recompression is lost and leakage loss is little and compression efficiency is high
Contracting machine.
Compressor of the present utility model possesses in closed container：Compression mechanical part, which is to the refrigeration that sucks from suction inlet
Agent is compressed and discharges the cold-producing medium from outlet；And motor part, which is via main shaft to compression mechanism section
It is driven, the compressor is characterised by that compression mechanism section 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 above-mentioned cylinder body and above-mentioned main shaft are supported, above-mentioned upper bearing (metal) tool
Have the upper shaft flange part 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
The lower axle flange part of the opening face closure of the other end, at least one party in above-mentioned upper shaft flange part and above-mentioned lower axle flange part
Flange part be formed with the groove portion for possessing above-mentioned outlet, in above-mentioned flange part, be located at above-mentioned groove portion across above-mentioned main shaft
Opposition side region thickness with gradually changing away from above-mentioned main shaft, with regard to axial direction, the above-mentioned flange of above-mentioned cylinder body
The formation in portion has the size of the cross sectional moment of inertia in the region of that side of above-mentioned groove portion and is located at above-mentioned groove portion across above-mentioned main shaft
Opposition side region cross sectional moment of inertia equal in magnitude.
Be preferably located at the region of the opposition side of the groove portion, be in the vertical view to the flange part by from the master
Axle centrally through two regions marking off of line of demarcation in, with respect to that side for being formed with the groove portion region across
The line of demarcation and be located at the region of opposition side.
The thickness of the flange part in the region of the opposition side of the groove portion is preferably located at away from the main shaft
Thinning.
Be preferably located at the region of the opposition side of the groove portion the flange part, compression mechanical part contrary
The face of side inclines.
Preferably, flange part fastening is linked to using fixed component the end of the cylinder body, is formed with the groove
The number ratio of the fixed component in the region of that side in portion is located at the region of the opposition side in the region across the main shaft
The number of the interior fixed component is many.
The thickness of the flange part in the region of the opposition side of the groove portion is preferably located at away from the line of demarcation
And it is thickening.
Be preferably located at the region of the opposition side of the groove portion the flange part, compression mechanical part contrary
The face of side inclines.
Preferably, flange part fastening is linked to using fixed component the end of the cylinder body, is formed with the groove
The number ratio of the fixed component in the region of that side in portion is located at the region of the opposition side in the region across the main shaft
The number of the interior fixed component is few.
Preferably, from the main shaft by and cross on line, described flange with the line of demarcation vertically intersects
The formation in portion has the sectional area in the region of that side of the groove portion and is located at the area of the opposition side in the region across the main shaft
The sectional area in domain is equal.
Be preferably located at the region of the opposition side of the groove portion the flange part, compression mechanical part contrary
The face of side is the inclined plane without step difference.
Be preferably located at the region of the opposition side of the groove portion the flange part, compression mechanical part contrary
The face of side, so that described in the amount bent to the compression mechanical part side of the groove portion side and the opposition side to the groove portion
The amount identical mode of compression mechanical part side flexure is inclined.
Preferably, the face of the compression mechanical part side of the flange part is single plane.
Compressor of the present utility model can reduce recompression loss and leakage loss and improve compression efficiency.
Description of the drawings
Fig. 1 is the longitudinal section of the compressor for illustrating embodiment of the present utility model 1.
Fig. 2 is the sectional elevation of the compressor for illustrating embodiment of the present utility model 1.
Fig. 3 is the side view of the bearing of Fig. 1.
Fig. 4 is the top view of the bearing of Fig. 1.
Fig. 5 is the side view of the variation of the bearing for illustrating Fig. 1.
Fig. 6 is the top view of the variation of the bearing for illustrating Fig. 1.
Fig. 7 is the schematic diagram of the longitudinal section of the upper bearing (metal) of the compressor of embodiment of the present utility model 2.
Fig. 8 is the schematic diagram of the longitudinal section of the model that upper bearing (metal) flange part is assumed to cantilever beam.
Description of reference numerals：
1 ... closed container；2 ... motor part；3 ... compression mechanical parts；4 ... main shafts；5 ... eccentric shafts；6 ... cylinder bodies；On 7 ...
Bearing；7a ... upper bearing (metal) flange part；7a1 ... discharge chambe side surface；7a2 ... boss side surface；7b ... upper bearing (metal) boss portion；8…
Lower bearing；8a ... lower bearing flange part；8b ... lower bearing boss portion；9 ... pistons；10 ... blade grooves；11 ... blades；12 ... springs
Part；13 ... discharge chambes；14 ... suction inlets；15 ... outlets；15a ... dump valve；16 ... groove portions；17 ... fixed components；17a～
17e ... fastens linking part；100 ... compressors.
Specific embodiment
Embodiment 1.
Fig. 1 is the longitudinal section of the compressor 100 for illustrating present embodiment.Fig. 2 is the sectional elevation of compressor 100.Pressure
Contracting machine 100 possesses motor part 2 and compression mechanical part 3 in closed container 1.Motor part 2 transmits rotor via main shaft 4
The revolving force of 2a, is thus driven to compression mechanical part 3.In compression mechanical part 3, discharge chambe 13 is configured to include：Hollow
The cylinder body 6 of drum；Upper bearing (metal) 7, its are arranged at the upper axial end of cylinder body 6；And lower bearing 8, which is arranged at lower end.Main shaft
4 upside is supported on upper bearing (metal) boss portion 7b in the way of rotating freely, and the downside of main shaft 4 is supported in the way of rotating freely
Lower bearing boss portion 8b.It is provided with discharge chambe 13：The piston 9 of ring-type, its in the way of sliding freely be fixed on main shaft 4
Eccentric shaft 5 chimeric and carry out eccentric rotary；And blade 11, its be accommodated in along cylinder body 6 the blade groove 10 for radially extending and
Piston 9 is pressed on by spring members 12.Low pressure is divided into by the blade 11 that piston 9 is pressed on by spring members 12 in discharge chambe 13
Space and high-pressure space.In the action of compressor 100, the revolving force of motor part 2 is transferred to piston 9 via main shaft 4.Living
Plug 9 carries out eccentric rotary in discharge chambe 13, so as to suction in from the suction inlet 14 formed in the side of cylinder body 6 to discharge chambe 13
The cold-producing medium of low pressure, by the rotation of piston 9 make low-voltage space in discharge chambe 13 and high-pressure space Volume Changes, one
While being compressed to cold-producing medium.The flange part in upper bearing (metal) 7 (below, is claimed by jack-up upward to be compressed to the cold-producing medium of high pressure
For upper bearing (metal) flange part 7a) the dump valve 15a that covers of the outlet 15 that formed and discharged to outside discharge chambe 13.
Compression mechanical part 3 is provided with bilevel discharge chambe 13.The structure of the discharge chambe 13 of lower floor and the pressure on upper strata
The structure of contracting room 13 is identical.Identical with upper bearing (metal) flange part 7a, in flange part (the hereinafter referred to as lower bearing flange part of lower bearing 8
Outlet and dump valve that the outlet covered 8a) are also formed with, and the cold-producing medium after compression is by dump valve jack-up upward
And discharged to outside discharge chambe 13.Additionally, Fig. 1 is provided with the example of the situation of bilevel discharge chambe 13, but can also
The structure of the discharge chambe 13 for being formed as being provided only with either one.In addition, eliminate in FIG closed container 1 top and under
The diagram in portion, but closed container 1 is the container of airtight construction.It is stored with the bottom of closed container 1 main to entering line slip fortune
Dynamic piston 9 implements the refrigerator oil (not shown) of lubrication.As cold-producing medium, for example, can use HFO-1234yf, HFO-
1123 grade unitary system cryogens or these unitary system cryogens above-mentioned and the mix refrigerant of HFC refrigerant, the propane such as R32
(R290) natural refrigerant such as hydrocarbon refrigerant or carbon dioxide such as.
Fig. 3 is the side view of the upper bearing (metal) 7 of compressor 100.Fig. 4 is the top view of the upper bearing (metal) 7 of compressor 100.Upper shaft
Hold flange part 7a the upper end of cylinder body 6 (Fig. 1) is linked to by fastening by the fixed components such as screw 17.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 is arranged.In order to prevent the fault caused because of the thermal expansion of the piston 9 rotated when compressor 100 operates, 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
The single plane for having inclined plane is constituted, and the opening surface of the axially upside of cylinder body 6 (Fig. 1) is covered by discharge chambe side surface 7a1.Separately
On the one hand, face 7a2 upper bearing (metal) flange part 7a, compression mechanical part 3 opposition side (upper bearing (metal) boss portion 7b side) (below, claims
For boss side surface 7a2) a part inclination.Specifically, upper bearing (metal) flange part 7a, be located at groove portion 16 across main shaft 4
The thickness in the region of opposition side is with gradually changing away from main shaft 4.In addition, specifically, in the vertical view to upper bearing (metal) 7 by
From main shaft 4 centrally through two regions marking off of line A-A (below, for convenience of description, referred to as line of demarcation A-A) in
, with respect to that side for being formed with groove portion 16 region D1 (hereinafter referred to as groove side region D1) across line of demarcation A-A be located at phase
The thickness of the upper bearing (metal) flange part 7a of the region D2 (hereinafter referred to as contrary side region D2) for tossing about, with away from line of demarcation A-A
And it is gradually thinning.Groove side region D1 and contrary side region D2 are the semicircle adjacent one another are with line of demarcation A-A as border respectively
Shape region.
Upper bearing (metal) flange part 7a, boss side surface 7a2 in contrary side region D2 with respect to groove side region D1 boss
Side surface 7a2 is inclined.As shown in figure 4, groove side region D1 can be set as and groove portion with the line of demarcation A-A of contrary side region D2
The center line B-B (below, for convenience of description, referred to as groove center line B-B) of 16 length direction is parallel.Hereinafter, in order to just
In explanation, by from main shaft 4 centrally through and the line C-C that vertically intersects with line of demarcation A-A be referred to as crossing line C-C.Upper shaft
The thickness H2 of the edge C2 for crossing contrary side region D2 on line C-C of flange part 7a is held than the edge C1's of groove side region D1
Thickness H1 is thin.In order to the rigidity for not making the upper bearing (metal) flange part 7a of contrary side region D2 excessively reduces, preferred thickness H2 is thickness
More than the 1/2 of H1.
In the fastening binding strength with respect to cylinder body 6, upper bearing (metal) flange part 7a groove side region D1 and contrary side region D2
Fastening binding strength equal or roughly equal in the case of, play following acting on.As the thickness H3 of groove portion 16 is than groove lateral areas
The thickness H1 of the upper bearing (metal) flange part 7a of domain D1 is thin, so groove portion 16 is easily bent to the direction of 13 side of discharge chambe, power is being caused
Upper bearing (metal) boss portion 7b is rolled to groove side region D1 and is played a role on oblique direction.On the other hand, due to contrary side region D2
The thickness H2 of upper bearing (metal) flange part 7a is with gradually thinning away from line of demarcation A-A, so power is causing upper bearing (metal) boss portion 7b
Roll to contrary side region D2 and play a role on oblique direction.According to said structure, due to the bending towards groove side region D1 side
Power is cancelled out each other with the bending force towards contrary side region D2 side, it is possible to preventing the discharge caused because being provided with groove portion 16
The situation that 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 such that it is able to reduce leakage loss.
The boss side surface 7a2 of upper bearing (metal) flange part 7a is preferably so that axial G, groove side region D1 with regard to cylinder body 6
The size of cross sectional moment of inertia incline with size identical angle F of the cross sectional moment of inertia of contrary side region D2.Groove side region
The size of D1 and the respective cross sectional moment of inertia of contrary side region D2 by fasten linking part 17a～respective position relationship of 17e, this
The parameters such as the size of position relationship and fastening binding strength of a little fastening linking parts and groove portion 16 determine.Upper bearing (metal) flange part 7a
Contrary side region D2 boss side surface 7a2 angle of inclination F can also by based on above-mentioned parameter simulation determining, energy
Enough simply consideration designs in the following manner.
As shown in Figure 4, it is believed that the number of the fastening linking part 17a～17c in groove side region D1 is than contrary lateral areas
In the case that the number of the fastening linking part 17d and 17e in the D2 of domain is many, the discharge chambe side surface 7a1 of groove side region D1 is easy
Bend to 13 side of discharge chambe.Under the above structure, as shown in figure 4, by making upper bearing (metal) flange part 7a, contrary lateral areas
The thickness of domain D2 enables to groove side region D1 and the contrary lateral areas with regard to axial G with thinning away from line of demarcation A-A
The flexure that D2 respective cross sectional moment of inertia in domain is equal and prevents discharge chambe side surface 7a1.Particularly fastening linking part 17a～
In the case of the respective fastening connection structure of 17e or fastening binding strength identical, prevent the effect for bending larger.
Fig. 5 is the side view of the variation for illustrating upper bearing (metal) 7.Fig. 6 is the top view of the variation for illustrating upper bearing (metal) 7.?
In the upper bearing (metal) 7 of Fig. 5 and Fig. 6, the incline direction of contrary side region D2 of upper bearing (metal) flange part 7a and fastening linking part
The configuration of 17a～17e is different from the upper bearing (metal) 7 of Fig. 3 and Fig. 4.As other structures are identical with above-mentioned embodiment, so saving
Slightly its explanation.
As shown in fig. 6, the fastening linking part 17a and 17b in groove side region D1 number than in contrary side region D2
Fastening linking part 17c～17e number few in the case of, the discharge chambe side surface 7a1 of groove side region D1 can be to discharge chambe
13 opposition side flexure.Under the above structure, as shown in fig. 6, by making upper bearing (metal) flange part 7a, contrary side region
The thickness of D2 is enabled to regard to axial G, groove side region D1 and contrary side region with thickening away from line of demarcation A-A
The flexure that the respective cross sectional moment of inertia of D2 is equal and prevents discharge chambe side surface 7a1.Particularly in fastening linking part 17a～17e
In the case of respective fastening connection structure or fastening binding strength identical, prevent the effect for bending larger.
In the structure of Fig. 3 and Fig. 4 and the structure of Fig. 5 and Fig. 6, in order that cross sectional moment of inertia is equal, can be simple
Ground is designed based on the size of sectional area.I.e., alternatively it is conceivable to, if the groove side that crosses on line C-C of upper bearing (metal) flange part 7a
Region D1 and the respective sectional area of contrary side region D2 equal, then with regard to axial G, groove side region D1 and contrary side region
The respective cross sectional moment of inertia of D2 is almost equal.In order that crossing groove side region D1 on line C-C and contrary side region D2 each
Sectional area equal, incline the boss side surface 7a2 of upper bearing (metal) flange part 7a such that it is able to so that with regard to axial G, groove side
Region D1 and the equal and flexure that prevents discharge chambe side surface 7a1 of the respective cross sectional moment of inertia of contrary side region D2.
As shown in Fig. 3 and Fig. 4 and Fig. 5 and Fig. 6, the boss side surface of contrary side region D2 of upper bearing (metal) flange part 7a
7a2 does not preferably have the inclined plane of step difference.According to said structure, do not produce in the upper bearing (metal) flange part 7a of contrary side region D2
The flex point of raw stress such that it is able to suppress the flexure of contrary side region D2 side, and be easily formed as and groove side region D1 side
Moment of flexure is equal to.In addition, though the boss side surface 7a2 of contrary side region D2 of upper bearing (metal) flange part 7a is inclined, but discharge chambe side
Surface 7a1 is not inclined, and therefore, it is possible to minimize the gap between discharge chambe side surface 7a1 and piston 9, is let out so as to be difficult to generation
Leakage loss is lost.So, according to the compressor 1 of present embodiment, recompression loss can not only be reduced, but also leakage can be reduced
Loss such that it is able to improve compression efficiency.
Above-mentioned embodiment is created as the situation of the structure for inclining the boss side surface 7a2 of upper bearing (metal) flange part 7a
Example, the boss side surface for lower bearing flange part 8a can also be formed as being allowed to inclining in the same manner as above-mentioned embodiment
Structure.Act on also by identical in this case and play 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
The c mode equal with maximum deflection d for being in the upper bearing (metal) 7 of the opposition side of groove portion 16 across main shaft 4, determines upper bearing (metal)
The thickness of flange part 7a.Maximum deflection c is 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 inner peripheral portion 7a3 of the discharge chambe side surface 7a1 of 16 side of groove portion when position and flexure.
Maximum deflection d is the position of inner peripheral portion 7a3 of the discharge chambe side surface 7a1 of the opposition side of the groove portion 16 when not bending and scratch
Vertical direction distance between the position of inner peripheral portion 7a3 of the discharge chambe side surface 7a1 of the opposition side of the groove portion 16 when bent.Upper shaft
The boss side surface 7a2 for holding 16 side of groove portion of flange part 7a is inclined as causing maximum deflection c identical with maximum deflection d.
Fig. 8 be upper bearing (metal) flange part 7a is assumed to general as fixing point with the peripheral part 7a4 of discharge chambe side surface 7a1
Cantilever beam model longitudinal section schematic diagram.In the model, if the cross sectional moment of inertia of the one side of upper bearing (metal) 7 is set to I,
Vertical coefficient of elasticity is set to E, the power that upper bearing (metal) flange part 7a is fixed on cylinder body 6 is set to P by fixed component 17, by fixed component 17
The horizontal range of peripheral part 7a4 of position to discharge chambe side surface 7a1 be set to a, by the position of fixed component 17 to discharge chambe
The horizontal range of inner peripheral portion 7a3 of side surface 7a1 is set to b, then maximum deflection y is formed as following formula.
【Mathematical expression 1】
Deflection can be calculated using above-mentioned mathematical expression, for example, can also be carried out using the construction calculating instrument such as CAE
Calculate.If defining specific size and deflection being calculated, the upper bearing (metal) flange part 7a of 16 side of groove portion can be realized
6.7 μm of upper bearing (metal) flange part 7a of opposition side of deflection and groove portion 16 of 8.1 μm of deflection.In groove portion 16
In the case that the boss side surface 7a2 of opposition side is not inclined, i.e. in thickness and the groove of the upper bearing (metal) flange part 7a of 16 side of groove portion
In the case of the thickness identical of the upper bearing (metal) flange part 7a of the opposition side in portion 16, the scratching of the opposite to that side of deflection of 16 side of groove portion
The difference of bent amount is larger.On the other hand, in the compressor 100 of present embodiment, the boss side surface 7a2 of the opposition 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 opposition side of groove portion 16 is formed as the upper bearing (metal) of 16 side of groove portion
The thickness of the 70% of the thickness of the edge C1 of flange part 7a.In this case, by calculating the opposition side that can obtain groove portion 16
Deflection be 8.3 μm.The deflection of 16 side of groove portion is 0.2 μ (about 3% with the difference of the deflection of the opposition side of groove portion 16
Difference), deflection is almost consistent.Preferably allow for deflection and reach 1 μm or so, and preferably make the difference of deflection in ± 10% with
Interior.
In the compressor 100 of the present embodiment, so that the deflection of the upper bearing (metal) flange part 7a of 16 side of groove portion and groove portion
The deflection identical mode of the upper bearing (metal) flange part 7a of 16 opposition side makes the boss side surface 7a2 of the opposition side of groove portion 16 incline
Tiltedly.According to said structure, equilibrium can be guaranteed in the opposition side of 16 side of groove portion and groove portion 16, as a result, discharge chambe can be made
Gap between side surface 7a1 and piston 9 becomes uniform such that it is able to reduce leakage loss.
Claims (12)
1. a kind of compressor, which possesses in closed container：Compression mechanical part, its are pressed to the cold-producing medium sucked from suction inlet
Contract and the cold-producing medium is discharged from outlet；And motor part, which is driven to the compression mechanical part via main shaft,
The compressor is characterised by,
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
State the axial both ends of cylinder body and the main shaft supported,
The upper bearing (metal) has the upper shaft flange part of the opening face closure of axial one end of the cylinder body, and the lower bearing has
By the lower axle flange part of the opening face closure of the axial other end of the cylinder body,
The flange part of at least one party in the upper shaft flange part and the lower axle flange part is formed with possesses the discharge
The groove portion of mouth,
The thickness in the region of opposition side in the flange part, being located at the groove portion across the main shaft is with away from the master
Axle and gradually change, with regard to axial direction, the described flange part of the cylinder body formation have the groove portion that side region cut
The size of face the moment of inertia is located at the size phase of the cross sectional moment of inertia in the region of the opposition side of the groove portion with across the main shaft
Deng.
2. compressor according to claim 1, it is characterised in that
Positioned at the region of the opposition side of the groove portion, be in the vertical view to the flange part by from the main shaft centrally through
Two regions marking off of line of demarcation in, with respect to that side for being formed with the groove portion region across the line of demarcation
Region positioned at opposition side.
3. compressor according to claim 1 and 2, it is characterised in that
Positioned at the region of the opposition side of the groove portion the flange part thickness with thinning away from the main shaft.
4. compressor according to claim 3, it is characterised in that
The flange part, compression mechanical part opposition side face positioned at the region of the opposition side of the groove portion inclines.
5. compressor according to claim 3, it is characterised in that
Flange part fastening is linked to the end of the cylinder body using fixed component,
The number ratio of the fixed component in the region of that side for being formed with the groove portion is located at the area across the main shaft
The number of the fixed component in the region of the opposition side in domain is many.
6. compressor according to claim 2, it is characterised in that
Positioned at the region of the opposition side of the groove portion the flange part thickness with thickening away from the line of demarcation.
7. compressor according to claim 6, it is characterised in that
The flange part, compression mechanical part opposition side face positioned at the region of the opposition side of the groove portion inclines.
8. compressor according to claim 6, it is characterised in that
Flange part fastening is linked to the end of the cylinder body using fixed component,
The number ratio of the fixed component in the region of that side for being formed with the groove portion is located at the area across the main shaft
The number of the fixed component in the region of the opposition side in domain is few.
9. compressor according to claim 2, it is characterised in that
From the main shaft by and the formation for crossing on line, described flange part that vertically intersects with the line of demarcation
The sectional area for stating the region of that side of groove portion is located at the sectional area phase in the region of the opposition side in the region with across the main shaft
Deng.
10. compressor according to claim 4, it is characterised in that
It is do not have positioned at the flange part, compression mechanical part opposition side the face in the region of the opposition side of the groove portion
There is the inclined plane of step difference.
11. compressors according to claim 4, it is characterised in that
Positioned at the flange part, compression mechanical part opposition side the face in the region of the opposition side of the groove portion, so that
Obtain the compression mechanical part of the amount and opposition side to the groove portion bent to the compression mechanical part side of the groove portion side
The amount identical mode of side flexure is inclined.
12. compressors according to claim 1 and 2, it is characterised 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 |
|---|---|---|---|
| PCT/JP2015/069997 WO2017009917A1 (en) | 2015-07-13 | 2015-07-13 | Compressor |
| JPPCT/JP2015/069997 | 2015-07-13 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206000729U true CN206000729U (en) | 2017-03-08 |
Family
ID=57757818
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620731694.0U Withdrawn - After Issue CN206000729U (en) | 2015-07-13 | 2016-07-12 | Compressor |
| CN201610546572.9A Active CN106351833B (en) | 2015-07-13 | 2016-07-12 | Compressor |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610546572.9A Active CN106351833B (en) | 2015-07-13 | 2016-07-12 | Compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6418329B2 (en) |
| CN (2) | CN206000729U (en) |
| WO (1) | WO2017009917A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106351833A (en) * | 2015-07-13 | 2017-01-25 | 三菱电机株式会社 | Compressor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Family Cites Families (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 |
| WO2011019114A1 (en) * | 2009-08-10 | 2011-02-17 | 엘지전자 주식회사 | Compressor |
| WO2017009917A1 (en) * | 2015-07-13 | 2017-01-19 | 三菱電機株式会社 | Compressor |
-
2015
- 2015-07-13 WO PCT/JP2015/069997 patent/WO2017009917A1/en active Application Filing
- 2015-07-13 JP JP2017528025A patent/JP6418329B2/en not_active Expired - Fee Related
-
2016
- 2016-07-12 CN CN201620731694.0U patent/CN206000729U/en not_active Withdrawn - After Issue
- 2016-07-12 CN CN201610546572.9A patent/CN106351833B/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106351833A (en) * | 2015-07-13 | 2017-01-25 | 三菱电机株式会社 | Compressor |
| CN106351833B (en) * | 2015-07-13 | 2018-07-20 | 三菱电机株式会社 | Compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106351833A (en) | 2017-01-25 |
| JPWO2017009917A1 (en) | 2017-09-14 |
| JP6418329B2 (en) | 2018-11-07 |
| WO2017009917A1 (en) | 2017-01-19 |
| CN106351833B (en) | 2018-07-20 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20170308 Effective date of abandoning: 20180720 |