CN104948460A - Compressor - Google Patents
Compressor Download PDFInfo
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- CN104948460A CN104948460A CN201510136858.5A CN201510136858A CN104948460A CN 104948460 A CN104948460 A CN 104948460A CN 201510136858 A CN201510136858 A CN 201510136858A CN 104948460 A CN104948460 A CN 104948460A
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- receiving hole
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- edge
- discharge route
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- 239000010687 lubricating oil Substances 0.000 claims abstract description 7
- 239000003507 refrigerant Substances 0.000 claims description 36
- 238000005192 partition Methods 0.000 claims description 18
- 238000003825 pressing Methods 0.000 claims description 16
- 230000007246 mechanism Effects 0.000 claims description 12
- 238000000926 separation method Methods 0.000 claims description 12
- 230000001360 synchronised effect Effects 0.000 claims description 4
- 238000005057 refrigeration Methods 0.000 abstract description 2
- 238000002955 isolation Methods 0.000 abstract 4
- 208000028659 discharge Diseases 0.000 description 58
- 230000000694 effects Effects 0.000 description 13
- 239000003921 oil Substances 0.000 description 13
- 230000008676 import Effects 0.000 description 9
- 239000000314 lubricant Substances 0.000 description 9
- 230000003321 amplification Effects 0.000 description 7
- 238000003199 nucleic acid amplification method Methods 0.000 description 7
- 230000000052 comparative effect Effects 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 4
- 239000006200 vaporizer Substances 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000005119 centrifugation Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 239000011148 porous material Substances 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 210000001364 upper extremity Anatomy 0.000 description 1
Abstract
The invention can improve lubricating oil isolation rate no matter an exhaust path structure is limited; the compressor spins refrigeration air so as to isolate the lubricating oil in an eccentric manner; the compressor comprises a first exhaust path 25a and a second exhaust path 25b formed in a containing hole 21 in a housing6, and an isolation cylinder23 fixed in the containing hole21 and formed to isolate the lubricating oil in an eccentric manner; the isolation cylinder 23 comprises a large diameter portion 23a, a small diameter portion 23c, and a connecting portion 23b connecting the large diameter portion with the small diameter portion; the isolation cylinder 23 enables the bottom P2 of a boundary edge to overlap with the top T1 and Top T2 of opening edges 26a and 26b of the first and second exhaust paths, or enables the boundary edge to be in the opening edges 26a and 26b of the first and second exhaust paths; the boundary edge forms the large diameter portion 23a and the connecting portion 23b.
Description
Technical field
The present invention relates to a kind of compressor.
Background technique
Japanese Patent Laid Open Publication No.2011-153618 discloses a kind of vane compressor of routine.This compressor comprises housing, compressing mechanism and centrifugal separator.Be formed with suction area, cylinder chamber, pressing chamber and discharge zone in the housing.Compressing mechanism is arranged in the housing.Compressing mechanism compresses the refrigerant gas in pressing chamber and the refrigerant gas compressed is expelled to discharge zone.Separator is also arranged in the housing.Separator is by making refrigerant gas turn and with centrifugation separation lubrication oil, thus being separated from refrigerant gas by lubricant oil in discharge zone.
More specifically, compressing mechanism comprises live axle, rotor and multiple blade.Live axle is arranged in the housing in the mode that can rotate around spin axis.Rotor is can be arranged in cylinder chamber with the mode of live axle synchronous rotary.Be formed with multiple blade groove in the rotor.Blade is arranged in corresponding blade groove in the mode that can advance and retract.Pressing chamber by the internal surface of cylinder chamber, rotor outer surface, be arranged on partition wall in front side and rear side and each blade is formed.Separator comprises splitter cylinder, turn path and discharge route, and refrigerant gas is around splitter cylinder turn in turn path, and discharge route is configured to the refrigerant gas from discharge zone to guide to turn path.
The refrigerant gas guiding to turn path from discharge route in turn path turn lubricant oil is separated in centrifugal mode.Isolated grease accumulation in the bottom of discharge chamber and be provided to need lubrication various parts.The refrigerant gas having isolated lubricant oil is discharged by the outlet of housing after passing splitter cylinder.
In process lubricant oil is separated from refrigerant gas with centrifugation, with regard to oily separation effect, it is desirable to refrigerant gas is derived together with the swirling flow produced around splitter cylinder.
But according to the opening direction of discharge route, refrigerant gas may cause turbulent flow after bumping against with splitter cylinder.Therefore, worry be that the number of turns that refrigerant gas completes in turn path will reduce, thus cause reduce oily separation effect.
The present invention makes based on above-mentioned conventional situation, and target of the present invention no matter has what structural limitations can both improve the separation effect of the lubricant oil in compressor to discharge route, wherein, this compressor is by making refrigerant gas turn and in centrifugal mode by lubricating oil separation out.
Summary of the invention
Compressor according to the present invention comprises: housing, is formed with pressing chamber in this housing; Compressing mechanism, this compressing mechanism arranges in the housing and is configured to compress the refrigerant gas in pressing chamber; Receiving hole, this receiving hole is formed in the housing; Discharge route, this discharge route has opening and with receiving hole via opening in communication, and it is configured to the refrigerant gas compressed in compressing mechanism to guide to receiving hole; And splitter cylinder, this splitter cylinder be fixed to receiving hole and be configured by make refrigerant gas in receiving hole turn and with centrifugal mode separation lubrication oil.
Splitter cylinder comprises fixing part, minor diameter and joint, and this fixing part is fixed to receiving hole, and minor diameter is configured to make refrigerant gas around its turn, and connection part structure becomes fixing part and minor diameter are connected to each other.
The part that fixing part is connected with joint is set to boundary edge.
Splitter cylinder is placed as and boundary edge and edge of opening is coincided or makes boundary edge within this edge of opening, and wherein this edge of opening is the edge of opening.
To illustrate the diagram that illustrates and all describing and inventive concept disclosed in accompanying drawing according to mode of execution disclosed in following description and accompanying drawing, in the accompanying drawings, other aspects of the present invention and advantage will be apparent.
Accompanying drawing explanation
Fig. 1 is the sectional view of the vane compressor according to mode of execution 1.
Fig. 2 is the sectional view of the vane compressor according to mode of execution 1 that the A-A along the line observed along arrow A direction in Fig. 1 intercepts.
Fig. 3 is the sectional view of the vane compressor according to mode of execution 1 that the B-B along the line observed along arrow B direction in Fig. 1 intercepts.
Fig. 4 is the sectional view of the vane compressor according to mode of execution 1 that the C-C along the line observed along arrow C direction in Fig. 1 intercepts.
Fig. 5 is the partial top view according to the back side panel in the vane compressor of mode of execution 1.
Fig. 6 is the sectional view of the amplification of main body according to the back side panel in the vane compressor of mode of execution 1.
Fig. 7 is the sectional view of the amplification of main body according to the back side panel in the vane compressor of mode of execution 1.
Fig. 8 is the sectional view of the amplification of main body according to the back side panel in the vane compressor of mode of execution 2.
Fig. 9 is the sectional view of the amplification of main body according to the back side panel in the vane compressor of comparative examples.
Figure 10 is the sectional view of the amplification of main body according to the back side panel in the vane compressor of mode of execution 3.
Figure 11 is the sectional view of the amplification of main body according to the back side panel in the vane compressor of mode of execution 4.
Figure 12 is the sectional view of the amplification of main body according to the back side panel in the vane compressor of mode of execution 5.
Embodiment
Hereinafter with reference to accompanying drawing, performance embodiments of the present invention 1 to 5 are described together in conjunction with comparative examples.
[mode of execution 1]
Be vane compressor according to the compressor of mode of execution 1.As shown in Figure 1, this compressor comprises front case 1, back side panel 3 and rear case 5.Front case 1, back side panel 3 and rear case 5 corresponds to housing 6.
Front case 1 comprises cylinder forming portion 7a in tubular and is arranged on the front end of cylinder forming portion 7a and the first partition wall 2 formed as one with cylinder forming portion 7a.In cylinder forming portion 7a, cylinder chamber 7 is recessed into before backward.As shown in Figures 2 and 3, cylinder chamber 7 is shaped to column, and its cross section orthogonal with the spin axis O of live axle 8 is oval.As shown in Figure 1, the first partition wall 2 is formed with the boss 1a stretched out forward.Axis hole 2b is formed as the front portion of live axle 8 is passed by this axis hole 2b in boss 1a.The first surface 2a orthogonal with spin axis O after first partition wall 2.
And, the outer circumferential face of cylinder forming portion 7a is arranged with the suction chamber 9 as the annular of suction area.As shown in Figure 2, suction chamber 9 is connected via two inhalation port 9c with cylinder chamber 7.
As shown in Figure 1, back side panel 3 comprises the second partition wall 3a and bump 3b, and wherein, this second partition wall 3a abuts the rear end of the cylinder forming portion 7a of front case 1.Second 4a orthogonal with spin axis O before second partition wall 3a.In the second partition wall 3a, the axis hole 4b of the rearward end 8a of accommodating live axle 8 is recessed into by forward direction.
The cylinder forming portion 7a of the accommodating back side panel 3 of rear case 5 and front case 1.Rear case 5 is formed assembly department 5a.Assembly department 5a is attached to the (not shown) such as the motor of vehicle.Discharge chamber 10 is formed between rear case 5 and back side panel 3.Cylinder chamber 7 and discharge chamber 10 are separated by the second partition wall 3a.
In rear case 5, be formed with entrance 9a and outlet 10a, this entrance 9a are configured to make suction chamber 9 lead to outside, and export 10a and be configured to make the top of discharge chamber 10 lead to outside.On the outer circumferential face of cylinder forming portion 7a, be combined with O type ring 13a and O type ring 13b in the front side of suction chamber 9 and rear side.O type ring 13a in the front seal of suction chamber 9 between rear case 5 and front case 1.O type ring 13b is sealed between rear case 5 and front case 1 at the rear side of suction chamber 9.And O type ring 13c is engaged on the outer circumferential face of the second partition wall 3a.O type ring 13c is sealed between the second partition wall 3a and rear case 5.
In the axis hole 2b of front case 1, be provided with shaft sealer 11 and sliding bearing 12a, and be provided with sliding bearing 12b in the axis hole 4b of back side panel 3.Live axle 8 is arranged in the mode that can rotate around spin axis O by shaft sealer 11 and sliding bearing 12a and 12b.The communication path 9b being configured to be communicated with suction chamber 9 and shaft sealer 11 is formed in the first partition wall 2.
As shown in Figures 2 and 3, rotor 15 is press-fitted into live axle 8.Rotor 15 is shaped to column, and its cross section orthogonal with spin axis O is circular, and its to be arranged in cylinder chamber 7 so as can with live axle 8 synchronous rotary.The outer circumferential face of rotor 15 is arranged with five blade groove 15a in the mode slightly tilted towards spin axis O.Blade 17 is contained in corresponding blade groove 15a in the mode that can advance and retract.Back pressure chamber 15d is formed between the bottom surface and corresponding blade groove 15a of each blade 17.Compressing mechanism 20 is formed by live axle 8, rotor 15 and blade 17.Lubricant oil in discharge chamber 10 is supplied to back pressure chamber 15d via back pressure feed lines (not shown).
Five pressing chambers 19 are formed by the outer circumferential face of paired adjacent blades 17, rotor 15, the inner peripheral surface of cylinder chamber 7, first surface 2a and second 4a.Pressing chamber 19 changes its capacity by the rotation of live axle 8, thus performs and be used for the sucting stage of refrigerant gas, compression stage and discharge stage.Suction chamber 9 communicates with each other via inhalation port 9c with the pressing chamber 19 being in sucting stage.
As shown in Figure 3, between the cylinder forming portion 7a and rear case 5 of front case 1, to be formed with between first row clearancen 14b between 14a and second row clearancen.First and second discharge space 14a, 14b communicates with each other via corresponding discharge port 10c to the pressing chamber 19 being in the discharge stage.Discharge in space 14a, 14b first and second and be provided with expulsion valve 10d and holder 10e, this expulsion valve 10d is configured to close the amount of raising that discharge port 10c, this holder 10e are configured to regulate expulsion valve 10d.
As shown in Figure 1 and Figure 4, the bump 3b expanded towards discharge chamber 10 with certain thickness is formed in the central authorities of back side panel 3.In bump 3b, be formed with receiving hole 21, this receiving hole 21 is configured in the vertical direction and extends and accommodating splitter cylinder 23 with tubular.This receiving hole 21 is used as oil separation chamber.The top of receiving hole 21 is import 21a, and splitter cylinder 23 is press fitted in import 21a.Receiving hole 21 is connected with discharge chamber 10 via the intercommunicating pore 21c being positioned at lower end.
Splitter cylinder 23 is formed by large-diameter portion 23a, convergent portion 23b and minor diameter 23c.Large-diameter portion 23a has the drum that diameter is approximately equal to the diameter of press fit import 21a.23b is coaxial with large-diameter portion 23a in convergent portion, is formed and the consecutive joint of large-diameter portion 23a.Convergent portion 23b has the drum of convergent.Minor diameter 23c is connected with convergent portion 23b and coaxial with large-diameter portion 23a and convergent portion 23b.Minor diameter 23c has the diameter drum less than the diameter of large-diameter portion 23a.As shown in Figure 6 and Figure 7, by being press fit tolerance limit from upper end position P1 to the range set of lower end position P2, large-diameter portion 23a to be press-fitted in import 21a and to be fixed to import 21a, thus forms fixing part.The lower end position P2 of large-diameter portion 23a corresponds to the upper end position of convergent portion 23b.The part that large-diameter portion 23a is connected at lower end position P2 place with convergent portion 23b is set to boundary edge.
The part being positioned at the inner peripheral surface of the receiving hole 21 below lower end position P2 forms outer cylindrical surface 31a.On the other hand, the outer circumferential face of the minor diameter 23c of splitter cylinder 23 forms interior cylindrical surface 31b.The interior cylindrical surface 31b being positioned at the inner side of outer cylindrical surface 31a has the drum coaxial with outer cylindrical surface 31a.The outer circumferential face of the convergent portion 23b of splitter cylinder 23 forms tubular connecting surface 31c.From the upper end of interior cylindrical surface 31b upwards continuously and little by little increase, and tubular connecting surface 31c is connected to outer cylindrical surface 31a for the diameter of tubular connecting surface 31c.31a, interior cylindrical surface 31b and tubular connecting surface 31c form turn path 31 on outer cylindrical surface.Formation air outlet, the upper end 23d of large-diameter portion 23a.As shown in Figure 1 and Figure 4, air outlet 23d is connected with the top of discharge chamber 10 and towards fluid output 10a.
First discharge route 25a, the second discharge route 25b, receiving hole 21, splitter cylinder 23 and turn path 31 form centrifugal separator 30.Discharge zone comprises 14b between 14a between first row clearancen, second row clearancen, the first discharge route 25a, the second discharge route 25b, turn path 31 and discharge chamber 10.
In back side panel 3, be formed with the first discharge route 25a and the second discharge route 25b, the first discharge route 25a is configured to refrigerant gas to derive 14a between first row clearancen, and the second discharge route 25b is configured to refrigerant gas to derive 14b between second row clearancen.First discharge route 25a linearly extends to turn path 31 from 14a between first row clearancen in the mode tilted slightly upward.And the second discharge route 25b linearly extends to turn path 31 from 14b between second row clearancen in the mode tilted slightly upward.As shown in Figure 5, the first discharge route 25a and the second discharge route 25b is connected to turn path 31 along corresponding tangent direction in the position of relative to each other 90 degree of displacements around turn path 31.
As shown in Figure 6 and Figure 7, when the Edge definition the first discharge route 25a and the second discharge route 25b being led to the opening of the position of receiving hole 21 is edge of opening 26a and edge of opening 26b, upper limb and the lower end position P2 of the upper end T1 of edge of opening 26a and the upper end T2 of edge of opening 26b and tubular connecting surface 31c coincide; In other words, upper end T1 and T2 of edge of opening 26a and 26b directly faces down end P2 or boundary edge.
Although not shown, outlet 10a is connected to condenser via pipeline, and condenser is connected to expansion valve via pipeline, and expansion valve is connected to vaporizer via pipeline, and vaporizer is connected to entrance 9a via pipeline.Condenser, expansion valve and vaporizer form external refrigeration loop.The refrigerating circuit comprising the vane compressor of mode of execution 1 forms vehicle air conditioner.
According in the vane compressor of mode of execution 1, when live axle 8 is driven by motor etc., rotor 15 and live axle 8 synchronous rotary, thus change the capacity of each pressing chamber 19.Therefore, the refrigerant gas through vaporizer is drawn in suction chamber 9 by entrance 9a, is then drawn in each pressing chamber 19 by inhalation port 9c.Then, in pressing chamber 19, be expelled to the first and second discharge space 14a and 14b by compressed refrigerant gas by discharge port 10c, and export to turn path 31 by the first and second discharge route 25a and 25b.Refrigerant gas is turn between cylindrical surface 31a and interior cylindrical surface 31b outside, so that in centrifugal mode by lubricating oil separation out.Isolated lubricant oil is flowing to outside the receiving hole 21 as oil separation chamber and through to accumulate in after intercommunicating pore 21c in the bottom of discharge chamber 10 and to be provided to the various parts needing lubrication.Refrigerant gas is upwards flowed and is discharged towards condenser from air outlet 23d by outlet 10a in splitter cylinder 23.
Like this, upper end T1 and T2 being configured so that edge of opening 26a and 26b of the first and second discharge route 25a and 25b due to vane compressor and the lower end position P2 of boundary edge be formed between large-diameter portion 23a and convergent portion 23b coincides, therefore, in turn path 31, there is turbulent flow hardly in the refrigerant gas being exported the first and second discharge route 25a and 25b.Therefore, by this vane compressor, be easy to make refrigerant gas turn and be easy to lubricant oil to separate in centrifugal mode in turn path 31.
So no matter have what structural limitations on discharge route, this vane compressor can both improve the separation effect of lubricant oil.
And for this vane compressor, because import 21a is formed in back side panel 3, and splitter cylinder 23 is press-fitted in import 21a, therefore by regulating the press fit tolerance limit of splitter cylinder 23 can realize aforesaid operations and effect.
In addition, in this vane compressor, the back side panel 3 limiting pressing chamber 19 forms the outer cylindrical surface 31a being configured to the receiving hole 21 of accommodating splitter cylinder 23.This allows vane compressor to manufacture to be less than conventional vane compressor.In addition, this vane compressor can reduce cost of production by the number reducing part.
Especially, for vane compressor, once back side panel 3 forms receiving hole 21, then limit the position forming discharge route 25a and 25b, thus refrigerant gas is derived along the direction tilted relative to splitter cylinder 23.But, for this vane compressor, because splitter cylinder 23 is placed in receiving hole 21, upper end T1 and T2 of edge of opening 26a and 26b of discharge route 25a and 25b and the lower end position P2 of boundary edge that is formed between large-diameter portion 23a and convergent portion 23b is coincided, therefore above edge of opening 26a and 26b of discharge route 25a and 25b, do not form exceptional space.A part for separator 30 and back side panel construct integratedly and form, thus avoid the turbulent flow of refrigerant gas.
[mode of execution 2]
As shown in Figure 8, according in the vane compressor of mode of execution 2, large-diameter portion 23a is press-fitted in import 21a, wherein, by from upper end position P1 to the range set of lower end position P2 be press fit tolerance limit.It is larger than the diameter of the first and second discharge route 25a and 25b in mode of execution 1 that first and second discharge route 25a and 25b are configured to its diameter.First and second discharge route 25a and 25b lead to receiving hole 21, and upper end T1 and T2 of edge of opening 26a and 26b of the first and second discharge route 25a and 25b is positioned at the top of the upper end of tubular connecting surface 31c, i.e. the top of the lower end position P2 of large-diameter portion 23a.That is, within splitter cylinder 23 is placed with and makes the boundary edge between large-diameter portion 23a and joint 23b be in edge of opening 26a and 26b of the first and second discharge route 25a and 25b.In other words, boundary edge be set in by edge of opening 26a and 26b around region scope in.Therefore, the top of edge of opening 26a and 26b is covered by large-diameter portion 23a, but edge of opening 26a with 26b is connected by the connection district identical with mode of execution 1 with turn path 31.Remaining configuration is identical with mode of execution 1.
Because the refrigerant gas be directed to beyond the first and second discharge route 25a and 25b turbulent flow occurs in turn path 31 hardly, therefore, this vane compressor achieves and the operation of mode of execution 1 and the similar operation of effect and effect equally.
And, due to for the ease of processing and save manipulation work upper end T1 and T2 of edge of opening 26a and 26b being placed on lower end position P2 place and the diameter increasing the first and second discharge route 25a and 25b of this vane compressor, therefore this vane compressor is easier to production than the vane compressor of mode of execution 1.
(comparative examples)
As shown in Figure 9, in the vane compressor of comparative examples, large-diameter portion 23a is press-fitted in import 21a, wherein, from upper end position P1 to the range set of lower end position P2 be press fit tolerance limit.First and second discharge route 25a and 25b lead to receiving hole 21, and upper end T1 and T2 of edge of opening 26a and 26b of the first and second discharge route 25a and 25b is positioned at below the upper end of tubular connecting surface 31c, namely below lower end position P2.Remaining configuration is identical with mode of execution 1.
This vane compressor saves manipulation work upper end T1 and T2 of edge of opening 26a and 26b being placed on lower end position P2 place, is therefore easier to produce than the vane compressor of mode of execution 1.
But, for this vane compressor, exceptional space S is created between upper end T1 and T2 and lower end position P2, thus the refrigerant gas in this space S is flowed along the direction different from the direction of swirling flow, and the refrigerant gas therefore, be directed into outside the first and second discharge route 25a and 25b is easy to cause the turbulent flow in turn path 31.Which reduce the number of turns that refrigerant gas completes in turn path 31, thus cause lubricating oil separation ability to decline.
[mode of execution 3]
As shown in Figure 10, according in the vane compressor of mode of execution 3, splitter cylinder 23 is formed by large-diameter portion 23a, curved part 23e and minor diameter 23c.Curved part 23e has the drum that diameter reduces, and it bends from large-diameter portion 23a to minor diameter 23c and forms the joint being configured to connect large-diameter portion 23a and minor diameter 23c.Remaining configuration is identical with 2 with mode of execution 1.
This vane compressor achieves and the operation of mode of execution 1 and 2 and the similar operation of effect and effect equally.
[mode of execution 4]
As shown in figure 11, according in the vane compressor of mode of execution 4, splitter cylinder 33 is formed by large-diameter portion 33a and convergent portion 33b.The outer circumferential face of the convergent portion 33b of splitter cylinder 33 is not only used as interior cylindrical surface 31b but also be used as tubular connecting surface 31c, and forms minor diameter and joint.The interior cylindrical surface 31b of this combination and tubular connecting surface 31c is positioned at the inner side of outer cylindrical surface 31a, and is shaped to the taper coaxial with outer cylindrical surface 31a.Remaining configuration is identical with 2 with mode of execution 1.
This vane compressor achieves and the operation of mode of execution 1 and 2 and the similar operation of effect and effect equally.
[mode of execution 5]
As shown in figure 12, according in the vane compressor of mode of execution 5, splitter cylinder 43 is formed by large-diameter portion 43a, joint 43b and minor diameter 43c.On the side of large-diameter portion 43a, joint 43b is almost at right angles to connected to large-diameter portion 43a, and in the side of minor diameter 43c, and joint 43b little by little and be connected to minor diameter 43c consistently.Remaining configuration is identical with 2 with mode of execution 1.
This vane compressor achieves and the operation of mode of execution 1 and 2 and the similar operation of effect and effect equally.
Describe the present invention with reference to mode of execution 1 to 5 above, but undoubtedly, the present invention is not limited to above-mentioned mode of execution 1 to 5 and can modifies as required when not departing from the spirit and scope of the invention and use.
Can not only vane compressor be embodied as according to compressor of the present invention, can also scroll compressor or tilted-plate compressor etc. be embodied as.
And in compressor according to the present invention, housing can be formed by front case, cylinder body, rear case, front side plate, back side panel etc.
Interior cylindrical surface is not necessarily cylindrical, can also be convergent.
Claims (3)
1. a compressor, comprising: housing, in described housing, be formed with pressing chamber; Compressing mechanism, described compressing mechanism to be arranged in described housing and to be configured to compress the refrigerant gas in described pressing chamber; Receiving hole, described receiving hole is formed in described housing; Discharge route, described discharge route has opening and described discharge route is connected with described receiving hole via described opening, and described discharge route is configured to the refrigerant gas compressed in described compressing mechanism to guide to described receiving hole; And splitter cylinder, described splitter cylinder is fixed to described receiving hole and is configured by and makes the turn and in centrifugal mode by lubricating oil separation out in described receiving hole of described refrigerant gas,
Wherein, described splitter cylinder comprises fixing part, minor diameter and joint, and described fixing part is fixed to described receiving hole, and described minor diameter is configured to make described refrigerant gas around described minor diameter turn, described connection part structure becomes described fixing part and described minor diameter are connected to each other
The part that described fixing part is connected with described joint is set to boundary edge, and
Described splitter cylinder is placed as and described boundary edge and edge of opening is coincided or makes described boundary edge within described edge of opening, and wherein, described edge of opening is the edge of described opening.
2. compressor according to claim 1, wherein:
Described housing forms cylinder chamber;
Described compressing mechanism comprises:
Live axle, described live axle is arranged in described housing in the mode that can rotate around spin axis,
Rotor, described rotor be arranged in described cylinder chamber can with described live axle synchronous rotary, wherein, described rotor is formed with multiple blade groove, and
Blade, described blade is arranged in corresponding blade groove in the mode that can advance and retract,
Described housing comprises the first partition wall and the second partition wall, and described cylinder chamber is formed between first surface and second, and described first surface is after described first partition wall, and described second is before described second partition wall,
Described pressing chamber is formed by the outer surface of the internal surface of described cylinder chamber, described rotor, described first surface, described second and described blade, and
Described discharge route is arranged by running through described second partition wall.
3. compressor according to claim 2, wherein, described receiving hole is formed in described second partition wall.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014069741A JP6201863B2 (en) | 2014-03-28 | 2014-03-28 | Compressor |
| JP2014-069741 | 2014-03-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104948460A true CN104948460A (en) | 2015-09-30 |
| CN104948460B CN104948460B (en) | 2017-06-20 |
Family
ID=54163406
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510136858.5A Expired - Fee Related CN104948460B (en) | 2014-03-28 | 2015-03-26 | Compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6201863B2 (en) |
| CN (1) | CN104948460B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109072920A (en) * | 2016-04-19 | 2018-12-21 | 欧伊特股份有限公司 | The separator of fluid, especially lubricant is separated from coolant fluid |
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|---|---|---|---|---|
| JPH04153596A (en) * | 1990-10-13 | 1992-05-27 | Toyota Autom Loom Works Ltd | Vane type compressor |
| CN1626821A (en) * | 2003-12-10 | 2005-06-15 | 三电有限公司 | Compressor |
| JP2005171859A (en) * | 2003-12-10 | 2005-06-30 | Sanden Corp | Compressor |
| JP2006144660A (en) * | 2004-11-19 | 2006-06-08 | Sanden Corp | Compressor |
| CN102326041A (en) * | 2009-02-27 | 2012-01-18 | 丹佛斯商业压缩机公司 | Device for separating lubricant from refrigerant lubricant/gas mixture discharged from at least one refrigerating compressor |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009138698A (en) * | 2007-12-10 | 2009-06-25 | Calsonic Compressor Inc | Gas compressor |
| JP2009185730A (en) * | 2008-02-07 | 2009-08-20 | Calsonic Kansei Corp | Compressor |
| JP5421223B2 (en) * | 2009-12-29 | 2014-02-19 | 株式会社ヴァレオジャパン | Vane type compressor |
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2014
- 2014-03-28 JP JP2014069741A patent/JP6201863B2/en not_active Expired - Fee Related
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2015
- 2015-03-26 CN CN201510136858.5A patent/CN104948460B/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04153596A (en) * | 1990-10-13 | 1992-05-27 | Toyota Autom Loom Works Ltd | Vane type compressor |
| CN1626821A (en) * | 2003-12-10 | 2005-06-15 | 三电有限公司 | Compressor |
| JP2005171859A (en) * | 2003-12-10 | 2005-06-30 | Sanden Corp | Compressor |
| JP2006144660A (en) * | 2004-11-19 | 2006-06-08 | Sanden Corp | Compressor |
| CN102326041A (en) * | 2009-02-27 | 2012-01-18 | 丹佛斯商业压缩机公司 | Device for separating lubricant from refrigerant lubricant/gas mixture discharged from at least one refrigerating compressor |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109072920A (en) * | 2016-04-19 | 2018-12-21 | 欧伊特股份有限公司 | The separator of fluid, especially lubricant is separated from coolant fluid |
| CN109072920B (en) * | 2016-04-19 | 2020-05-22 | 欧伊特股份有限公司 | Separator device for separating a fluid, in particular a lubricant, from a coolant fluid |
| US10935027B2 (en) | 2016-04-19 | 2021-03-02 | OET GmbH | Separator device for separating a fluid, in particular a lubricant, from a coolant |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104948460B (en) | 2017-06-20 |
| JP2015190418A (en) | 2015-11-02 |
| JP6201863B2 (en) | 2017-09-27 |
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