CN107269526B - Vane compressor - Google Patents
Vane compressor Download PDFInfo
- Publication number
- CN107269526B CN107269526B CN201710191924.8A CN201710191924A CN107269526B CN 107269526 B CN107269526 B CN 107269526B CN 201710191924 A CN201710191924 A CN 201710191924A CN 107269526 B CN107269526 B CN 107269526B
- Authority
- CN
- China
- Prior art keywords
- cylinder body
- recess portion
- face
- rotor
- blade
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C18/344—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 inner member
- F04C18/3446—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 inner member the inner and outer member being in contact along more than one line or surface
- F04C18/3447—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 inner member the inner and outer member being in contact along more than one line or surface the vanes having the form of rollers, slippers or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention provides vane compressor, it can be ensured that the lubricity between rotor and side plate.In the end face (13s) of bottom wall part (13p), the recess portion (13b) that can be circulated for lubricating oil is formed with around rotary shaft (16).In the end face (15s) of back side panel (15), the recess portion (15b) that can be circulated for lubricating oil is formed with around rotary shaft (16).Step is formed in recess portion (13b, 15b), so that depth is formed as multistage.It is provided with using step positioned at cricoid 1st stage portion of the outermost side and positioned at the position compared to the 1st inner side of stage portion and than the 2nd stage portion of the 1st stage portion depth in recess portion (13b, 15b).2nd stage portion has multiple arc sections via discontinuous part therebetween.The outer rim of recess portion (13b) is located at the position of the inner side of outer rim compared to rotor (18).
Description
Technical field
The present invention relates to vane compressors.
Background technique
In the past, about vane compressor, structure below is disclosed: in the inner space of cylinder block can rotate
Mode stores rotor, stores blade (for example, referring to Japanese Unexamined Patent Publication 2014- in the blade groove for the outer peripheral surface for being formed in rotor
No. 194177 bulletins (patent document 1)).Bottom surface and blade groove in the compressor documented by patent document 1, using blade
Bottom surface forms back pressure chamber, supplies lubricating oil towards back pressure chamber.
Patent document 1: Japanese Unexamined Patent Publication 2014-194177 bulletin
The region of the central side in region, i.e. rotor around back pressure chamber is carried out by the lubricating oil leaked from back pressure chamber
The lubrication of sliding part between blade and blade groove.But in vane compressor, sliding part is not only present in blade and leaf
Between film trap, and there is also sliding positions between the rotor and blade and side plate of rotation, generate burn in order to prevent, need
Ensure lubricity.
Summary of the invention
It is an object of the invention to can ensure the vane compressor of the lubricity between rotor and side plate.
Vane compressor according to the present invention has shell, rotary shaft, rotor, blade and discharge chambe.Shell tool
Have the cylinder body of tubular, be incorporated into the both ends of cylinder body and together with cylinder body divide formed cylinder body room the 1st dividing wall and
2nd dividing wall.Rotary shaft is supported on shell, and can be rotatably provided in cylinder body room.Rotor is fixed on rotary shaft.In rotor
Periphery be formed with blade groove.Blade is inserted into blade groove.Utilize the inner peripheral surface of cylinder body, the end face of the 1st dividing wall,
The end face of 2 dividing walls, the outer peripheral surface of rotor and blade divide in cylinder body room and form discharge chambe.At the end of the 1st dividing wall
At least any one party in face and the end face of the 2nd dividing wall is formed with the recess portion that can be circulated for lubricating oil around rotary shaft.?
Step is formed in recess portion, to form multistage depth.Step is provided with cricoid 1st positioned at the outermost side in recess portion
Rank portion and positioned at compared to the 1st inner side of stage portion position and than the 1st stage portion depth the 2nd stage portion.2nd stage portion
Have in such a way that there is the opposed state opposed with the blade groove and non-opposed state not opposed with the blade groove more
A arc sections, across discontinuous part between multiple arc sections.Discontinuous part has the depth equal with the 1st stage portion.
The outer rim of recess portion is located at the position of the inner side of outer rim compared to rotor.
In above-mentioned vane compressor, cylinder body is formed as one with the 1st dividing wall.It is compressed in above-mentioned vane type
In machine, arc sections are formed by a pair of of arc-shaped part.Alternatively, arc sections are formed by a pair of of fan shape part.
In accordance with the invention it is possible to ensure the lubricity between rotor and side plate.
Detailed description of the invention
Fig. 1 is the sectional view for showing the compressor based on embodiment.
Fig. 2 is the sectional view along the compressor of the II-II line of Fig. 1.
Fig. 3 is the sectional view along the compressor of the III-III line of Fig. 1.
Fig. 4 is to amplify the sectional view shown near the recess portion of back side panel.
Fig. 5 is to amplify the sectional view shown near the recess portion of bottom wall part.
Wherein, the reference numerals are as follows:
10: compressor；11: shell；12: back casing；12a: peripheral wall；13: procapsid；13a, 15a: oil scupper；13ac,
15ac: discontinuous part；13b, 14a, 14b, 15b: recess portion；13p: bottom wall part；13s, 15s: end face；14: cylinder body；14c: interior
Circumferential surface；14d: cylinder body room；15: back side panel；15aa: almost fan shape；15ab: path circular shape part；15d: oil
Supply passageway；15e: back pressure supply hole；16: rotary shaft；17a: gland seal device；18: rotor；18a: blade groove；18c: outer peripheral surface；
19: blade；20: sucking space；21: discharge chambe；22: suction inlet；23: inlet hole；30: discharge room；31: outlet；32: discharge
Valve；34: outlet；41: back pressure chamber；131,151: the 1 stage portion；132,152: the 2 stage portion；133: the 3 stage portions；
141b: it is extended face；142b: mounting surface；O: axle center.
Specific embodiment
Hereinafter, being illustrated referring to attached drawing to embodiment.In the presence of identical to identical component and corresponding part mark
Reference numeral and be not repeated the case where explanation.In the figure not with the record of actual dimension scale, for easy understanding
It constructs and records a part of ratio differently.
[structure of compressor 10]
Fig. 1 is the sectional view for showing the compressor 10 based on embodiment.Fig. 2 is the compression along the II-II line of Fig. 1
The sectional view of machine 10.Fig. 3 is the sectional view along the compressor 10 of the III-III line of Fig. 1.Compressor 10 is vane type compression
Machine.Compressor 10 is equipped on vehicle, the air-conditioning device for vehicle.
In addition, in the following description, left direction in the figure of compressor 10 shown in FIG. 1 is referred to as front, it will be shown in Fig. 1
Compressor 10 figure in right direction be referred to as rear.The axial of the following description, radial direction and circumferential expression rotary body that is, rotation
Shaft 16 and the axial of rotor 18, radial direction and circumferential direction.
As shown in Figure 1, the shell 11 of compressor 10 is by the back casing 12 (shell) of bottomed cylindrical and and back casing
The formation of procapsid 13 that 12 front end face combines.Back casing 12 has peripheral wall 12a (also referring to Fig. 2, Fig. 3).Procapsid 13 has
The bottom wall part 13p of the inner space of the cylinder body 14 and blocking cylinder body 14 of tubular.Procapsid 13 is formed as having round-ended cylinder
Shape.Bottom wall part 13p constitutes the 1st dividing wall.Cylinder body 14 is accommodated in back casing 12.Bottom wall part 13p is formed as with cylinder body 14
One.The material of back casing 12 and procapsid 13 is, for example, metal.
The cylinder body 14 of tubular extends from bottom wall part 13p.Cylinder body 14 have with the open end of bottom wall part 13p opposite side
Portion that is, open end.Configuration back side panel 15 is opposed to the open end of cylinder body 14.Back side panel 15 uses spiral shell (not shown)
Bolt is fixed on the open end of cylinder body 14.Back side panel 15 constitutes the 2nd dividing wall.Procapsid 13 and back side panel 15 are by rotary shaft
16 bearings are that can rotate.Rotary shaft 16 penetrates through in cylinder body 14.It is close that lip shape is provided between rotary shaft 16 and procapsid 13
The gland seal device 17a of envelope type.Gland seal device 17a prevents the leakage of the refrigerant gas of the circumferential surface along rotary shaft 16.
Bottom wall part 13p has the end face 13s for the side for dividing cylinder body room 14d.End face 13s is towards rear.Back side panel 15 has
There is the end face 15s for the another party for dividing cylinder body room 14d.End face 15s is towards front.The end face 13s of one side and the end face of another party
15s interval is set in parallel and mutually opposed.
The cylinder body 14 of tubular marks off cylinder body room 14d using bottom wall part 13p and back side panel 15.It is set in cylinder body room 14d
Set the rotor 18 with cylindric shape.Rotor 18 can integrally rotatably be installed on rotary shaft 16.The front end face of rotor 18
It is opposed with the end face 13s of bottom wall part 13p.The rear end face of rotor 18 is opposed with the end face 15s of back side panel 15.
As shown in FIG. 2 and 3, the inner peripheral surface 14c of cylinder body 14 is formed as ellipticity.It is provided with and turns in cylinder body room 14d
Son 18.Multiple blade groove 18a are formed in the outer peripheral surface 18c of rotor 18 in a manner of extending radially.In multiple blade groove 18a
It is able to be accommodated with blade 19 with haunting.The lubricating oil in aftermentioned discharging area 35 is supplied respectively to towards multiple blade groove 18a.
Along with the rotation of rotary shaft 16, rotor 18 rotates, and several blades in multiple blades 19 are by towards blade groove 18a's
Outside extrudes.When the inner peripheral surface 14c of the front end face of blade 19 and cylinder body 14 is contacted, in outer peripheral surface 18c, the cylinder body of rotor 18
The inner peripheral surface 14c in portion 14, adjacent pair blade 19, the end face 13s (Fig. 1) of bottom wall part 13p and back side panel 15 end face 15s
Multiple discharge chambes 21 are marked off between (Fig. 1).On the direction of rotation of rotor 18, the stroke that discharge chambe 21 expands volume is sucking
Stroke, the stroke that discharge chambe 21 reduces volume is compression travel.
The outer peripheral surface 18c of rotor 18 forms the wall surface of the inner circumferential side of discharge chambe 21.The inner peripheral surface 14c of cylinder body 14 forms pressure
The wall surface of the peripheral side of contracting room 21.The end face 13s of bottom wall part 13p forms the wall surface of the front side of discharge chambe 21.Back side panel 15
End face 15s forms the wall surface of the rear side of discharge chambe 21.Discharge chambe 21 is formed in cylinder body room 14d.
As shown in Figure 1 and Figure 2, the suction inlet 22 of perforation peripheral wall 12a is formed in back casing 12.In the outer of suction inlet 22
Circumferential portion is connected with connector portions 24.Sucking piping 25 is connected in connector portions 24.Refrigerant gas is flowed into via sucking piping 25
In suction inlet 22.Suction inlet 22 forms the refrigerant passage passed through for refrigerant.Being provided in suction inlet 22 prevents refrigerant
Refluence check valve (not shown).
Complete cycle in the circumferential direction that the outer peripheral surface of cylinder body 14 spreads cylinder body 14 is formed with recess portion 14a.Utilize recess portion 14a
And the inner peripheral surface of back casing 12 marks off sucking space 20.Sucking space 20 is connected to suction inlet 22.Cylinder body 14 and rear shell
The inner peripheral surface of body 12 cooperates, and sucking space 20 is marked off in back casing 12 (shell).
Sucking space 20 is formed between the cylinder body 14 radially and back casing 12 of rotary shaft 16.
As shown in Fig. 2, sucking space 20 is formed as cyclic annular between cylinder body 14 and back casing 12, and circumferentially.
Sucking space 20 is formed as surrounding the complete cycle of discharge chambe 21.
In the axial direction of rotary shaft 16, suck space 20 and suction inlet 22 be configured to it is Chong Die with discharge chambe 21.In cylinder body
Portion 14 is formed with a pair of of the inlet hole 23 (Fig. 2) being connected to sucking space 20.In suction stroke, discharge chambe 21 and sucking space
20 are connected to via inlet hole 23.Inlet hole 23 radially penetrates through cylinder body 14.Inlet hole 23 is opened in the inner peripheral surface 14c of cylinder body 14
Mouthful, and be open in sucking space 20.
Inlet hole 23, sucking space 20 and suction inlet 22 are formed in radial outside relative to discharge chambe 21.Inlet hole 23,
Sucking space 20 and suction inlet 22 are present in and make to divide between the end face 13s of bottom wall part 13p and the end face 15s of back side panel 15
Discharge chambe 21 radially extend and in the region that is formed.
As shown in figure 3, the outer peripheral surface recess in cylinder body 14 is provided with a pair of of recess portion 14b (also referring to Fig. 1).A pair of of recess portion
14b is mutually located at opposite side across rotary shaft 16.What each recess portion 14b was extended by the outer peripheral surface from cylinder body 14 towards rotary shaft 16
The mounting surface 142b for being extended face 141b and intersecting with extended face 141b and extending towards the outer peripheral surface of cylinder body 14
It is formed.
A pair of of discharge room 30 is marked off using the inner peripheral surface of extended face 141b, mounting surface 142b and back casing 12.
Discharge room 30 is located between cylinder body 14 and back casing 12 radially (also referring to Fig. 1).It is formed with and is installing in cylinder body 14
Face 142b opening and by discharge chambe 21 with the outlet 31 that is connected to of room 30 is discharged.Outlet 31 is by being installed on the row of mounting surface 142b
Valve 32 is opened and closed out.Dump valve 32 is moved back by the compressed refrigerant gas pressure of discharge chambe 21, via outlet 31 towards discharge 30 row of room
Out.
Room 30 is discharged and is located at the position compared to sucking space 20 side rearward.Sucking space 20 and discharge room 30 are formed in axis
Different position upwards.Sucking space 20, which is located at, compares discharge room 30 close to the position of bottom wall part 13p.Discharge room 30, which is located at, to be compared
Space 20 is sucked close to the position of back side panel 15.
As shown in Figure 2,3, the bottom surface that is accommodated in each blade 19 of each blade groove 18a and the bottom surface of each blade groove 18a it
Between be formed with back pressure chamber 41.Each blade 19 can be gone out by the pressure change in each back pressure chamber 41 relative to each blade groove 18a
Not yet.As shown in Figure 1, the end face 13s in bottom wall part 13p is formed with oil scupper 13a.Adjacent back pressure chamber 41 be formed to via
Oil scupper 13a is interconnected.
As shown in Figure 1, being formed in the end face 15s of back side panel 15 in radially inner circumference side includes the recess portion of oil scupper 15a
15b.As shown in figure 3, being formed as round centered on the axle center O of rotation center of the recess portion 15b to constitute rotary shaft 16 and rotor 18
Shape, outer rim are formed as cyclic annular.Recess portion 15b is formed with step, and thus depth is formed as multistage.Fig. 4 is that amplification shows back side panel
Sectional view near 15 recess portion 15b.In the present embodiment, as shown in figure 4, being formed with cricoid in radially side
1 stage portion 151 is being formed with 2nd stage portion 152 deeper than the 1st stage portion 151 compared to the inner side of the 1st stage portion 151.2nd
Stage portion 152 is equivalent to oil scupper 15a.The edge that the outer rim of recess portion 15b is located at the peripheral part compared to oil scupper 15a leans on radial outside
Position.
As shown in figure 3, oil scupper 15a is by surrounding rotary shaft 16 and two almost fan shape portion centered on the O of axle center
15aa and the path circular shape part 15ab of connection almost fan shape 15aa is divided to be formed.Path circular shape portion
15ab is divided to be formed in the position compared to the inner side back pressure supply hole 15e.The peripheral side of path circular shape part 15ab is close
Like the discontinuous discontinuous part 15ac of fan shape part 15aa.
Blade groove 18a repeated along with the rotation of rotary shaft 16 state opposed with almost fan shape 15aa with
And state not opposed with almost fan shape 15aa.Almost fan shape 15aa have following function: when with leaf
When film trap 18a is opposed, it is taken into the lubricating oil extruded out of blade groove 18a, on the other hand, lubricating oil is supplied towards blade groove 18a, adjusts
Back pressure in completeblade slot 18a.The arc sections of almost fan shape 15aa composition present embodiment.
Path circular shape part 15ab is formed in the position compared to the inner side back pressure supply hole 15e.Path is arc-shaped
Shape part 15ab and discontinuous part 15ac is located at the comparable position of discharge stroke with compressor 10.In discharge stroke,
It needs to maintain the back pressure in blade groove 18a higher and reliably divides discharge chambe 21, therefore be formed as blade groove 18a and oil extraction
Slot 15a (almost fan shape 15aa) not opposed structure.
Adjacent back pressure chamber 41 is formed to be interconnected via oil scupper 15a.In the radially inner most of blade groove 18a
Form the wide width part of the width extension of slot.As shown in Figure 2,3, from end on observation, the wide width part of blade groove 18a is formed as approximate circle
Shape.The outer rim of recess portion 15b is located at the position that the wide width part compared to blade groove 18a leans on radial outside.The outer rim of recess portion 15b is compared
The outer rim of rotor 18 is formed as path.
Each blade groove 18a is formed to be connected to the oil scupper 13a of bottom wall part 13p, and can be with back side panel 15
Oil scupper 15a connection.The forward end of back pressure chamber 41 can be connected to the oil scupper 13a of bottom wall part 13p.The rear square end of back pressure chamber 41
It can be connected to the oil scupper 15a of back side panel 15.
In compression travel, blade 19 receives stress from the inner peripheral surface 14c of cylinder body 14, radially medial movement.From court
Lubricating oil actuating pressure of the bottom surface of the blade 19 moved in blade groove 18a into back pressure chamber 41.At this point, lubricating oil is from back pressure chamber
41 outflows, and flowed into via oil scupper 13a, 15a towards the relatively low back pressure chamber 41 of pressure.In such manner, it is possible to apply flexibly oil scupper 13a,
15a carries out the adjustment of the pressure in back pressure chamber 41.
As shown in Figure 1, being also formed in the end face 13s of bottom wall part 13p in radially inner circumference side includes the recess portion of oil scupper 13a
13b.The outer rim of recess portion 13b is formed as cyclic annular.Recess portion 13b is formed with step, and thus depth is formed as multistage.Fig. 5 is that amplification is shown
Sectional view near the recess portion 13b of bottom wall part 13p out.As shown in figure 5, the end face 15s with back side panel 15 is identical, it is formed with ring-type
The 1st stage portion 131 and the deep positioned at the position compared to the inner side of the 1st stage portion 131 and than the 1st stage portion 131 the 2nd
Stage portion 132.2nd stage portion 132 is equivalent to oil scupper 13a.
As shown in Fig. 2, recess portion 13b forms the round centered on the O of axle center around rotary shaft 16.Oil scupper
13a is formed by two discontinuous arc-shaped parts.That is, existing between two arc-shaped parts has and the 1st
The discontinuous part 13ac of the identical depth in rank portion 131.Blade groove 18a is repeated along with the rotation of rotary shaft 16 and arc-shaped
The opposed state in part and state not opposed with arc-shaped part.Arc-shaped part has the back in adjustment blade groove 18a
The function of pressure.The arc sections of arc-shaped part composition present embodiment.
3rd stage portion more shallow than the 2nd stage portion 132 that is, oil scupper 13a is also formed in the inner circumferential side of oil scupper 13a
133.The depth of 3rd stage portion 133 is set to equal with the 1st stage portion 131.That is, oil scupper 13a can be described as by recessed
The bottom surface of portion 13b is further arranged recess portion and is formed.The outer rim of recess portion 13b is located at the edge of the peripheral side compared to oil scupper 13a
By the position of radial outside.The outer rim of recess portion 13b is located at the position that the wide width part compared to blade groove 18a leans on radial outside.Recess portion
The outer rim of 13b is formed as path compared to the outer rim of rotor 18.
As shown in Figure 1, the peripheral wall 12a in back casing 12 is formed with outlet 34.Connector is continuously provided in outlet 34
Portion 38.The discharge towards the extension of the outside (such as the condenser in external refrigerant circuit) of compressor 10 is connected in connector portions 38
Piping 39.
Discharging area 35 is formed using the division of back side panel 15 in the rear side of back casing 12.Oil is equipped in discharging area 35
Separator 36.Oil eliminator 36 is arranged to separate lubricating oil contained in refrigerant gas.Oil eliminator 36 has
The shell 36a of bottomed cylindrical.Cylindric oily cylinder 36b is fixed in the open side of shell 36a.
Oily access 36c is formed in the lower part of shell 36a.Oily access 36c is by the bottom in shell 36a with discharging area 35
Side connection.It is formed with access 37 in back side panel 15 and shell 36a (also referring to Fig. 3).Access 37 is by discharge room 30 and outside
Connection in shell 36a.Oily supply passageway 15d and back pressure supply hole 15e are formed in back side panel 15.Oily supply passageway 15d and
Back pressure supply hole 15e guides the lubricating oil for being stored in the bottom side of discharging area 35 to blade groove 18a.
[movement of compressor 10]
The movement of compressor 10 is illustrated below.When rotary shaft 16 rotates, rotor 18 and blade 19 rotate, from
The outside (for example, external refrigerant circuit) of compressor 10 sucks refrigerant gas towards sucking space 20 via suction inlet 22.Quilt
The refrigerant gas for being sucked into sucking space 20 is drawn into each discharge chambe 21 in suction stroke via inlet hole 23.It is sucked into
The refrigerant gas of each discharge chambe 21 is compressed by the volume reducing of the discharge chambe 21 of the rotation along with rotor 18.Compression
Refrigerant gas afterwards is discharged via outlet 31 towards each discharge room 30 from each discharge chambe 21.
Refrigerant gas in each discharge room 30, towards flowing out in shell 36a, is ejected into oily cylinder 36b via access 37
Outer peripheral surface, and on one side oily cylinder 36b outer peripheral surface revolution while guide to the lower section in shell 36a.At this point, passing through
Centrifuge separation is oily from refrigerant gas separation lubrication.From the lubricating oil after refrigerant gas separation towards the bottom sidesway of shell 36a
It moves, and is stored in the bottom of discharging area 35 via oily access 36c.
Be stored in the lubricating oil of the bottom of discharging area 35 from oily supply passageway 15d via back pressure supply hole 15e guide to
Blade groove 18a is also supplied towards oil scupper 13a, 15a.Using the pressure of the lubricating oil in blade groove 18a by blade 19 towards peripheral side
It extrudes.Discharge chambe 21 is marked off using the blade 19 for being forced into peripheral side.Using the lubricating oil of guidance to blade groove 18a to leaf
Piece 19 and the slipper of blade groove 18a are lubricated.Supply to the lubricating oil in oil scupper 15a is also directed to recess portion 15b
It is interior, rotor 18 and the slipper of back side panel 15 are lubricated using the lubricating oil.It supplies to the lubricating oil in oil scupper 13a
Also it is directed in recess portion 13b, rotor 18 and the slipper of bottom wall part 13p is lubricated using the lubricating oil.
In oil eliminator 36, the refrigerant gas after separation lubrication oil moves upward in the inside of oily cylinder 36b,
It is discharged via outlet 34 towards the outside (for example, external refrigerant circuit) of compressor 10.
[effect and effect]
Then, the effect and effect of the compressor 10 of above-mentioned embodiment are illustrated.
In the compressor 10 of present embodiment, as shown in Figure 1, being formed in the end face 15s of back side panel 15 inside in diameter
Side includes the recess portion 15b of oil scupper 15a, also, being formed in the end face 13s of bottom wall part 13p in radially inner circumference side includes row
The recess portion 13b of oil groove 13a.
By forming recess portion 13b, 15b, and it is formed so that lubricating oil can circulate in recess portion 13b, 15b, it can be true
Protect the lubricity between the end face of rotor 18 and the end face 13s of the end face 15s and bottom wall part 13p of back side panel 15.Utilize storage
Lubricating oil in recess portion 13b, 15b can promote the bearing for being supported on the rotary shaft 16 of bottom wall part 13p and back side panel 15
Lubrication.
As described above, oil scupper 13a, 15a have the function of adjusting the pressure in back pressure chamber 41.By oil scupper 13a,
Recess portion 13b, 15b are formed on the basis of 15a, the interior of oil scupper 13a, 15a and recess portion 13b, 15b can be accommodated in by being capable of increasing
The amount of the lubricating oil in portion.It is easy to cope with the variation along with the lubricants capacity in the back pressure chamber 41 of the movement of blade 19 as a result, because
This can promote the pressure in back pressure chamber 41 to adjust.
Oil scupper 13a, 15a have multiple arc sections.Multiple arc sections be arranged between across discontinuous part 13ac,
15ac, so as to state blade groove 18a opposed with oil scupper 13a, 15a and blade groove 18a not with oil scupper 13a, 15a couple
The state set.As a result, in the discharge stroke of compressor 10, the refrigerant gas of high pressure can will be compressed into discharge chambe 21
Body is discharged towards discharge room 30, it can be ensured that the performance of compressor 10.
If the outer rim of recess portion 13b, 15b are greater than the outer rim of rotor 18, when blade 19 is extruded and court from blade groove 18a
When radial outside is mobile, the meeting hooking of blade 19 hinders the movement of blade 19 in the step of recess portion 13b, 15b and end face 13s, 15s.
By the way that the outer rim of recess portion 13b, 15b to be formed as less than to the outer rim of rotor 18 as in the present embodiment, can swimmingly carry out
Blade 19 haunts relative to blade groove 18a's.
If recess portion 13b, 15b not radially inner circumference side include oil scupper 13a, 15a and by recess portion 13b, 15b and oil scupper
13a, 15a points are opened, then the connection of recess portion 13b, 15b and oil scupper 13a, 15a can be interfered, to interfere lubricating oil towards oil scupper
The inflow of 13a, 15a.Include oil scupper 13a, 15a, energy in radially inner circumference side by recess portion 13b, 15b as in the present embodiment
It is enough towards lubricating oil is easily imported in recess portion 13b, 15b, it is accordingly possible to ensure rotor 18 and back side panel 15 and bottom wall part 13p
Between lubricity.By increasing the diameter of recess portion 13b, 15b as far as possible in the range smaller than the outer diameter of rotor 18, it is able to suppress
The sliding contact and resulting sliding of the end face 13s of the end face 15s and bottom wall part 13p of rotor 18 and back side panel 15 hinder
Power.
In addition, oil film is formed between rotor 18 and back side panel 15 and bottom wall part 13p in the rotation of rotor 18, because
This, it is difficult to generate the contact of rotor 18 with back side panel 15 and bottom wall part 13p.In the stopping of rotor 18, there are rotor 18 because
The pressure difference of lubricating oil and be axially moveable, the case where either side in rotor 18 and bottom wall part 13p and back side panel 15 contacts.
Therefore, after rotor 18 just starts rotation, contact is most easily produced.As in the present embodiment, it is formed than oil scupper 13a, 15a
Big recess portion 13b, the 15b of outer rim, thus, it is possible to reduce end face 13s, 15s of rotor 18 and bottom wall part 13p and back side panel 15
The area of contact, also, radially outside supplies and is formed the lubricating oil imported from oil scupper 13a, 15a towards recess portion 13b, 15b
Oil film becomes easy, therefore can effectively inhibit contact.
In addition, as shown in Figure 1, cylinder body 14 is formed as one with bottom wall part 13p.It is formed in the end face 13s of bottom wall part 13p
There is the recess portion 13b in rounded shape centered on the O of axle center.By forming recess portion 13b, and towards importing lubricating oil, energy in recess portion 13b
Enough ensure the lubricity between rotor 18 and bottom wall part 13p.Even if cylinder body 14 and bottom wall part 13p are formed by casting etc.
In the case where being integrated, by contact the tool relative to bottom wall part 13p relative rotation with end face 13s come to end face 13s into
Row machining, is also able to easily form the recess portion 13b of round.
In addition, as shown in Figure 1, the depth ratio that the 1st stage portion 131,151 of recess portion 13b, 15b are recessed from end face 13s, 15s
The depth as shallow that oil scupper 13a, 15a are recessed from end face 13s, 15s.If recess portion 13b, 15b are too deep, from recess portion 13b, 15b court
The quantitative change for the lubricating oil that bearing portion is escaped from is more, and the function of lubrication oil reduces in recess portion 13b, 15b.Blade 19 towards relative to
The direction of radial skew tilts, as a result, there is the case where generating noise.By as in the present embodiment by recess portion 13b,
The depth of 15b is defined as more shallow than oil scupper 13a, 15a, is able to suppress the generation of noise, and blade 19 can be made swimmingly to move.
In addition, in the above description, the bottom wall part 13p example being formed as one with cylinder body 14 is illustrated.
Also it can replace the example, then be formed as such as flowering structure: bottom wall part 13p is separately formed as front side board and cylinder body 14,
Cylinder body 14 is configured between the front side board and back side panel 15 of interval configuration in the axial direction.
Also two almost fan shapes be can use and connect the path circular arc of two almost fan shapes
Shape forms oil scupper 13a.Also two arc-shaped parts be can use and form oil scupper 15a.
More than, embodiment is illustrated, above-mentioned disclosure all only illustrates in terms of whole, not
It is defined.Technical scope of the invention is indicated by the scope of the claims, it is intended to encompass is equal with the scope of the claims
Whole changes in the meaning and range.
Claims (4)
1. a kind of vane compressor, wherein
The vane compressor has:
Shell, cylinder body with tubular and is incorporated into the both ends of the cylinder body and divides together with the cylinder body
Form the 1st dividing wall and the 2nd dividing wall of cylinder body room；
Rotary shaft is supported on the shell, and can be rotatably provided in the cylinder body room；
Rotor is fixed on the rotary shaft, is formed on the outer periphery blade groove；
Blade is inserted into the blade groove；
Discharge chambe utilizes the inner peripheral surface of the cylinder body, the end face of the 1st dividing wall, described in the cylinder body room
The end face of 2 dividing walls, the outer peripheral surface of the rotor and the blade divide；And
Back pressure chamber is formed between the bottom surface of the blade groove and the bottom surface of the blade,
The wide width part of the width extension of slot is formed in the radially inner most of the blade groove, constitutes the back pressure chamber,
At least any one party in the end face of the 1st dividing wall and the end face of the 2nd dividing wall surrounds the rotary shaft
The recess portion that can be circulated for lubricating oil is formed,
Step is formed within the recess, to form multistage depth, is provided with and is located at most using the step in the recess portion
Cricoid 1st stage portion of peripheral side and positioned at compared to the inner side of the 1st stage portion position and than described 1st
2nd stage portion of rank portion depth, the 2nd stage portion are configured to the oil scupper that the adjacent back pressure chamber communicates with each other, and
Have in such a way that there is the opposed state opposed with the blade groove and non-opposed state not opposed with the blade groove more
A arc sections, across discontinuous part between multiple arc sections, discontinuous part has the depth equal with the 1st stage portion
Degree,
The outer rim of the recess portion is located at the position of the inner side of outer rim compared to the rotor, and compares the institute of the blade groove
State the position that wide width part leans on radial outside.
2. vane compressor according to claim 1, wherein
The cylinder body is formed as one with the 1st dividing wall.
3. vane compressor according to claim 1 or 2, wherein
The arc sections are formed by a pair of of arc-shaped part.
4. vane compressor according to claim 1 or 2, wherein
The arc sections are formed by a pair of of fan shape part.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016072316A JP6634933B2 (en) | 2016-03-31 | 2016-03-31 | Vane type compressor |
| JP2016-072316 | 2016-03-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107269526A CN107269526A (en) | 2017-10-20 |
| CN107269526B true CN107269526B (en) | 2019-07-16 |
Family
ID=60004113
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710191924.8A Expired - Fee Related CN107269526B (en) | 2016-03-31 | 2017-03-28 | Vane compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6634933B2 (en) |
| CN (1) | CN107269526B (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4717321A (en) * | 1982-06-18 | 1988-01-05 | Diesel Kiki Co., Ltd. | Vane compressor with vane back pressure adjustment |
| JP2008169811A (en) * | 2007-01-15 | 2008-07-24 | Calsonic Compressor Inc | Gas compressor |
| CN101469705A (en) * | 2007-12-26 | 2009-07-01 | 上海三电贝洱汽车空调有限公司 | Rotary vane type compressor |
| CN103775337A (en) * | 2012-10-19 | 2014-05-07 | 株式会社丰田自动织机 | Vane compressor |
-
2016
- 2016-03-31 JP JP2016072316A patent/JP6634933B2/en active Active
-
2017
- 2017-03-28 CN CN201710191924.8A patent/CN107269526B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4717321A (en) * | 1982-06-18 | 1988-01-05 | Diesel Kiki Co., Ltd. | Vane compressor with vane back pressure adjustment |
| JP2008169811A (en) * | 2007-01-15 | 2008-07-24 | Calsonic Compressor Inc | Gas compressor |
| CN101469705A (en) * | 2007-12-26 | 2009-07-01 | 上海三电贝洱汽车空调有限公司 | Rotary vane type compressor |
| CN103775337A (en) * | 2012-10-19 | 2014-05-07 | 株式会社丰田自动织机 | Vane compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6634933B2 (en) | 2020-01-22 |
| JP2017180419A (en) | 2017-10-05 |
| CN107269526A (en) | 2017-10-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR100675548B1 (en) | Compressor | |
| JP6402648B2 (en) | Vane type compressor | |
| CN104343680A (en) | Oil pump | |
| JP5708570B2 (en) | Vane type compressor | |
| JP6852636B2 (en) | Vane compressor | |
| CN107269526B (en) | Vane compressor | |
| EP2520802A1 (en) | Lubricating oil supply structure of vane-type compressor | |
| CN108506209B (en) | Blade-tape compressor | |
| CN108506210B (en) | Blade-tape compressor | |
| JP2015137564A (en) | Vane type compressor | |
| JP2004052675A (en) | Gas compressor | |
| JP2018168801A (en) | Vane type compressor | |
| JP5751215B2 (en) | Tandem vane compressor | |
| JP5585617B2 (en) | Tandem vane compressor | |
| CN109854506A (en) | Vane compressor | |
| KR101750683B1 (en) | Compressor | |
| JP6388000B2 (en) | Compressor | |
| JP5196049B2 (en) | Refrigerant gas suction amount control device for rotary compressor | |
| US11994119B2 (en) | Compressor | |
| JP2010001836A (en) | Gas compressor | |
| JP2018168780A (en) | Vane type compressor | |
| JP2009041576A (en) | Scroll type compressor | |
| US20150125331A1 (en) | Displacement pump | |
| JP2008014174A (en) | Compressor | |
| JP2016125403A (en) | Vane type compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20190716 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |