CN1309961C - Leaking oil proof sturctrue for vacuum pump - Google Patents

Leaking oil proof sturctrue for vacuum pump Download PDF

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Publication number
CN1309961C
CN1309961C CNB021437874A CN02143787A CN1309961C CN 1309961 C CN1309961 C CN 1309961C CN B021437874 A CNB021437874 A CN B021437874A CN 02143787 A CN02143787 A CN 02143787A CN 1309961 C CN1309961 C CN 1309961C
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CN
China
Prior art keywords
oil
stop
pump
sealing
running shaft
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Expired - Fee Related
Application number
CNB021437874A
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Chinese (zh)
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CN1487202A (en
Inventor
山本真也
川口真广
内山理
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Toyota Industries Corp
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Toyoda Automatic Loom Works Ltd
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Application filed by Toyoda Automatic Loom Works Ltd filed Critical Toyoda Automatic Loom Works Ltd
Priority to CNB021437874A priority Critical patent/CN1309961C/en
Publication of CN1487202A publication Critical patent/CN1487202A/en
Application granted granted Critical
Publication of CN1309961C publication Critical patent/CN1309961C/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Abstract

The present invention relates to a vacuum pump for sucking gas by operating gas conveying bodies (23 to 32) in pump chambers (39 to 43) through rotation of rotary shafts (19, 20). The vacuum pump is provided with housing members (14, 33) for storing oil, wherein an oil area (331) adjacent to the pump chambers (39 to 43) is limited by the housing members (14, 33) for storing oil; the rotary shafts (19, 20) are provided with convex parts penetrated through the housing members (14, 33) for storing oil and extended into the oil area (331) from the pump chambers (39 to 43); barrier parts (67, 68, 72) are positioned on the rotary shafts (19, 20) and integrally rotate with the rotary shafts (19, 20), and the barrier parts (67, 68, 72) are used for preventing the oil from entering the pump chambers (39 to 43); the barrier parts (67, 68, 72) are axially arranged along the rotary shafts (19, 20).

Description

Vacuum pump with leak-proof arrangement
Technical field
The present invention relates to a kind of structure that prevents leakage of oil of vacuum pump, this vacuum pump sucks gas by means of the rotation of running shaft by the gas transfer body of handling in pump chamber.
Background technique
In a kind of typical vacuum pump, use lubricant oil to come lubricating movement part.In Japanese publication No.63-129829 and No.3-11193, disclose to have and prevent that oil from entering and do not wish that there is the vacuum pump of the structure in zone in lubricant oil.
At publication number is among the No.63-129829 in the disclosed vacuum pump, is used to prevent that oil from entering starts a diskware in chamber to be arranged on running shaft, especially, when oil along the surface of running shaft when starting the chamber to move, will arrive this diskware.The centrifugal force that is produced by the rotation of this diskware makes oil be splashed to be formed on that in the circular groove on this diskware, this oil will flow to the bottom of circular groove, outside being discharged into then and along the eliminating passage that is connected in this bottom.
At publication number is that disclosed vacuum pump has an annular chamber and an oil propeller that is provided at this annular chamber that is used for to the bearing fuel feeding among the No.3-11193, when oil along the surface of running shaft from this annular chamber when a turbulence pump moves, oil is thrown away by this oil propeller, and this oil that is thrown out of will be sent to a motor cavity by a discharge orifice that is connected in this annular chamber then.
This diskware (oil propeller) that rotates integratedly with running shaft is one to prevent that oil from entering the mechanism in undesirable zone, when the centrifugal force that is produced by the rotation of a diskware (oil propeller) is used to prevent that oil from entering certain zone, its effect will be subjected to this diskware (oil propeller) and around the influence of the shape of this diskware (oil propeller) wall.
JP-B-6-6950 discloses a kind of vacuum pump, but fails to solve problem recited above.
Summary of the invention
Therefore, the purpose of this invention is to provide a kind of mechanism that prevents oil leakage, it can prevent effectively that oil from entering into the pump chamber of vacuum pump.
In order to obtain above-mentioned and other purpose, and according to purpose of the present invention, the invention provides a kind of vacuum pump, this vacuum pump of rotation by means of running shaft sucks gas by the gas transfer body of handling in pump chamber, it is characterized in that it comprises: hold the housing member of oil, the wherein said housing member that holds oil limits an oil district in abutting connection with described pump chamber, and described running shaft has a lug boss, and this lug boss protrudes into the described oil district from the housing member of pump chamber through holding oil; And a plurality of stop parts, described stop part is positioned on the described running shaft, to rotate integratedly with running shaft, and prevent that oil from entering into described pump chamber, wherein said stop part is along the axially locating of described running shaft, and by diameter from arranging towards the order that the oil district reduces gradually that near a side of pump chamber wherein each stop part has an outer surface; And a plurality of annular oil cavities, each annular oil cavity centers in the described outer surface, and wherein said oil pocket is arranged towards the order that the oil district reduces gradually from the side near pump chamber by diameter.
With the explanation of following example to the principle of the invention, other aspects and advantages of the present invention clearly present in conjunction with the drawings.
Description of drawings
Below, in conjunction with the drawings with reference to the explanation of the preferred embodiment, the present invention may be better understood and its purpose and advantage.
Fig. 1 (a) is a section plan of multi-stage roots pump according to a first embodiment of the invention;
Fig. 1 (b) is a partial sectional view that amplifies of pump shown in Fig. 1 (a);
Fig. 2 (a) is the sectional view along 2a-2a line intercepting among Fig. 1 (a);
Fig. 2 (b) is the sectional view along 2b-2b line intercepting among Fig. 1 (a);
Fig. 3 (a) is the sectional view along 3a-3a line intercepting among Fig. 1 (a);
Fig. 3 (b) is the sectional view along 3b-3b line intercepting among Fig. 1 (a);
Fig. 4 (a) is the sectional view along 4a-4a line intercepting among Fig. 3 (b);
Fig. 4 (b) is a partial sectional view that amplifies of pump shown in Fig. 4 (a);
Fig. 5 (a) is the sectional view along 5a-5a line among Fig. 3 (b);
Fig. 5 (b) is a partial sectional view that amplifies of pump shown in Fig. 5 (a);
Fig. 6 is a sectional view that amplifies of pump shown in Fig. 1 (a);
Fig. 7 is a perspective exploded view, wherein shows part back cover spare, first shaft sealing and a leakproof ring of pump shown in Fig. 1 (a);
Fig. 8 is a perspective exploded view, wherein shows part back cover spare, second shaft sealing and a leakproof ring of pump shown in Fig. 1 (a);
Fig. 9 is second an embodiment's of the present invention amplification view;
Figure 10 is the 3rd an embodiment's of the present invention amplification view;
Figure 11 is the 4th an embodiment's of the present invention amplification view;
Figure 12 is the 5th an embodiment's of the present invention amplification view; With
Figure 13 is the 6th an embodiment's of the present invention amplification view.
Embodiment
Now, with reference to the accompanying drawings 1 (a) to 8 explanations according to multistage Roots pumps (Roots pump) 11 of first embodiment of the invention.
Shown in Fig. 1 (a), this pump 11 is vacuum pumps, and it comprises a rotor housing spare 12, a front case spare 13 and a rear case spare 14, and this front case spare 13 is connected in the front end of this rotor housing spare 12.The open front of one end cap, 36 sealing front case spares 13.This rear case spare 14 is connected in the rear end of this rotor housing spare 12.This rotor housing spare 12 comprises a cylinder body 15 and chamber confining wall 16, and the quantity of wall is four in this embodiment.Shown in Fig. 2 (b), this cylinder body 15 comprises a pair of cylinder body piece 17,18, and each chamber confining wall 16 comprises a pair of wall portion 161,162.Shown in Fig. 1 (a), first pump chamber 39 is formed between the chamber confining wall 16 of this front case spare 13 and high order end.As shown in the figure, second, third and the 4th pump chamber 40,41,42 are respectively formed between two adjacent chamber confining walls 16, and from left to right arrange according to this order.The 5th pump chamber 43 is formed between the chamber confining wall 16 of this rear case spare 14 and low order end.
First running shaft 19 is rotatably supported by a pair of radial bearing 21,37 of this front case spare 13 and this rear case spare 14, and is same, and second running shaft 20 is also rotatably supported by a pair of radial bearing 21,37 of this front case spare 13 and this rear case spare 14.This first and second running shaft 19,20 is parallel each other, and this running shaft 19,20 passes chamber confining wall 16 and extends.This radial bearing 37 is supported by bearing support 45.Two bearing jacks 47,48 are formed in the end 144 of this rear case spare 14.Bearing support 45 is suitable for respectively being installed in this bearing jack 47,48.
The first, second, third, fourth and the 5th rotor 23,24,25,26,27 and this first running shaft 19 form, equally, the first, second, third, fourth and the 5th rotor 28,29,30,31,32 and this second running shaft 20 also form.Axis 191,201 directions along this running shaft 19,20 see that the shape and size of rotor 23-32 are identical.This first rotor 23,28 is contained in this first pump chamber 39, and is engaged with each other; This second rotor 24,29 is contained in this second pump chamber 40, and is engaged with each other; This third trochanter 25,30 is contained in the 3rd pump chamber 41, and is engaged with each other; This fourth trochanter 26,31 is contained in the 4th pump chamber 42, and is engaged with each other; The 5th rotor 27,32 is contained in the 5th pump chamber 43, and is engaged with each other.This first to the 5th pump chamber 39-43 is unlubricated, therefore, rotor 23-32 any one contact in this cylinder body 15, chamber confining wall 16, front case spare 13 and the rear case spare 14 of being arranged to get along well, in addition, this each to the rotor that engages slide relative not each other.
Shown in Fig. 2 (a), this first rotor 23,28 defines a suction area 391 and a compressing area 392 in this first pump chamber 39, and the pressure in this compressing area 392 is higher than the pressure in this suction area 391.Equally, this second is determining suction area 391 and compressing area 392 to fourth trochanter 24-26,29-31 in corresponding pump chamber 40-42.Shown in Fig. 3 (a), the 5th rotor 27,32 has been determined a suction area 431 and a compressing area 432 in the 5th pump chamber 43, and they and suction area 391 and compressing area 392 are similar.
Shown in Fig. 1 (a), one gear housing spare 33 is connected on this rear case spare 14, a pair of through hole 141,142 is formed on this rear case spare 14, this running shaft 19,20 extends through this through hole 141,142 and this first and second bearings jack 47,48 respectively, thereby this running shaft 19,20 stretches into respectively in this gear housing spare 33 to form bump 193,203.Gear 34,35 is individually fixed on this bump 193,203, and is meshing with each other.One electric motor M is connected on this gear housing spare 33, one shaft coupling 44 is sent to the driving force of this motor M on this first running shaft 19, direction shown in the middle arrow R1 drives this first running shaft, 19 rotations to this motor M along Fig. 2 (a) to 3 (b), gear 34,35 is sent to rotatablely moving of first running shaft 19 on second running shaft 20, thus the direction rotation shown in the middle arrow R2 of this second running shaft 20 along Fig. 2 (a) to 3 (b).Therefore, this first and second running shaft 19,20 is along opposite direction rotation, and this gear 34,35 makes running shaft 19,20 integrally rotate.
Shown in Fig. 4 (a) and 5 (a), one gear receiving cavity 331 is formed in this gear housing spare 33, this gear receiving cavity 331 maintains the lubricant oil Y that is used for oilgear 34,35, and this gear 34,35 has formed a gear mechanism that is contained in this gear receiving cavity 331.This gear receiving cavity 331 and this bearing jack 47,48 form an oil seal district, and this gear housing spare 33 and this rear case spare 14 form an oil pocket or the Yi You district that is adjacent to the 5th pump chamber 43.Gear 34,35 rotation is splashing lubricant oil in this gear receiving cavity 331, thus this oil lubrication radial bearing 37.
Shown in Fig. 2 (b), a passage 163 is formed on the inside of this each chamber confining wall 16, and each chamber confining wall 16 all has and is connected in 164 and one outlet 165 of one on the passage 163 inlet.Each pump chamber 39-43 to adjacency is connected to each other by the passage 163 in the corresponding chamber confining wall 16.
Shown in Fig. 2 (a), an inlet 181 extends through the cylinder body portion 18 of this cylinder body 15, and is connected in this first pump chamber 39.Shown in Fig. 3 (a), an outlet 171 extends through the cylinder body portion 17 of this cylinder body 15, and is connected in the 5th pump chamber 43.When gas enters this first pump chamber 39 from this inlet 181, rotatablely moving of the first rotor 23,28 makes this gas enter into compressing area 392.In this compressing area 392, gas is compressed and its pressure is higher than pressure in suction area 391.After this, this gas is by inlet 164, passage 163 in corresponding chamber confining wall 16 with export 165 and be sent in the suction area of second pump chamber 40.Then, this gas flows and compression repeatedly to the 3rd, the 4th, the 5th pump chamber 41,42,43 in this order from this second pump chamber 40.The volume of this first to the 5th pump chamber 39-43 reduces in this order gradually, and when gas arrived the suction area 431 of the 5th pump chamber 43, rotatablely moving of the 5th rotor 27,32 made this gas enter into compressing area 432.After this this gas is from exporting 171 outsides that are discharged into this vacuum pump 11.In other words, the function of each rotor 23-32 all is as a gas transfer member that is used for transmitting gas.
The function of this outlet 171 is that conduct is used for the discharge passage of gaseous emission to these vacuum pump 11 outsides, and the 5th pump chamber 43 is the afterbody pump chambers that are connected in this outlet 171.In the compressing area of this first to the 5th pump chamber 39-43, the pressure in the compressing area 432 of the 5th pump chamber 43 is the highest, and the function of this compressing area 432 is as a region of maximum compression.This outlet 171 is connected in this region of maximum compression 432 that is limited by the 5th rotor 27,32 in the 5th pump chamber 43.
Shown in Fig. 1 (a), first and second annular shaft sealing 49,50 is fixedly fitted to respectively on this first and second running shaft 19,20, and this shaft sealing 49,50 lays respectively in this first and second bearings jack 47,48.One seal ring 51 is arranged between the circumferential surface 192 of the internal circular surfaces of first shaft sealing 49 and first running shaft 19, and is same, and a seal ring 52 is arranged between the circumferential surface 202 of the internal circular surfaces of second shaft sealing 50 and second running shaft 20.Each seal ring 51,52 prevents that all lubricant oil Y from leaking into the 5th pump chamber 43 from this corresponding jack 47,48 along the circumferential surface 192,202 of corresponding running shaft 19,20.
Shown in Fig. 4 (b), between the peripheral wall 471 of the external peripheral surface 491 of the large-diameter portion 60 of first shaft sealing 49 and first jack 47, there is the gap.Shown in Fig. 5 (b), between the peripheral wall 481 in the external peripheral surface 501 of the large-diameter portion 80 of second shaft sealing 50 and second hole 48, also there is the gap.Equally, between the bottom surface 472 of the front surface 492 of first shaft sealing 49 and this first jack 47, there is the gap, between the bottom surface 482 of the front surface 502 of second shaft sealing 50 and this second jack 48, has the gap.This shaft sealing 49,50 is rotated integratedly with running shaft 19,20 respectively.
Annular protrusion 53 stretches out from the bottom 472 of this first jack 47 coaxially, and annular protrusion 54 stretches out from the bottom 482 of this second jack 48 in an identical manner coaxially.Circular groove 55 is formed on 472 opposing end faces 492 of bottom this first shaft sealing 49 and first jack 47 coaxially, and circular groove 56 is formed on the relative front surface 502 in bottom this second shaft sealing 50 and second hole 48 482 in an identical manner coaxially.Each annular protrusion 53,54 stretches in the corresponding groove 55,56, and the top of this projection 53,54 is positioned at the position near these groove 55,56 bottoms.Each projection 53 is separated into chamber, a pair of labyrinth 551,552 with the inside of the respective grooves 55 of this first shaft sealing 49, and each projection 54 is separated into chamber, a pair of labyrinth 561,562 with the inside of the respective grooves 56 of this second shaft sealing 50.First labyrinth sealing 57 that this projection 53 and groove 55 form corresponding to first running shaft 19, second labyrinth sealing 58 that this projection 54 and groove 56 form corresponding to second running shaft 20.The function of the front-end face 492,502 of this shaft sealing 49,50 is the sealing surfaces as shaft sealing 49,50, and the function of the bottom 472,482 of bearing jack 47,48 is the sealing surfaces as this rear case spare 14.In this embodiment, the plane that front surface 492 and bottom 472 form perpendicular to first running shaft, 19 axis 191, same, the plane that front surface 502 and bottom 482 form perpendicular to these running shaft 20 axis 201.In other words, this front surface 492 and bottom 472 are to form the surface along the sealing that the radial direction of first shaft sealing 49 is extended, and be same, and this front surface 502 and bottom 482 are to form the surface along the sealing that the radial direction of second shaft sealing 50 is extended.
As Fig. 4 (b) with shown in 7, one first spiral chute 61 is formed on the external peripheral surface 491 of large-diameter portion 60 of this first shaft sealing 49; As Fig. 5 (b) with shown in 8, one second spiral chute 62 is formed on the external peripheral surface 501 of large-diameter portion 60 of this second shaft sealing 50.Along the sense of rotation R1 of this first running shaft 19, this first spiral chute 61 forms from lead to the guiding channel of the 5th pump chamber 43 corresponding to gear receiving cavity 331 1 sides.Along the sense of rotation R2 of this second running shaft 20, this second spiral chute 62 forms from lead to the guiding channel of the 5th pump chamber 43 corresponding to gear receiving cavity 331 1 sides.Therefore, when running shaft 19,20 rotations, each spiral chute 61,62 all forms a pumping installations, and from transmitting fluid corresponding to this gear receiving cavity 331 of the 5th pump chamber 43 1 side direction.Promptly, each spiral chute 61,62 all forms a pumping installations, and it promotes lubricant oil should move in the oil district from the side direction corresponding to the 5th pump chamber 43 between the peripheral wall 471,481 of the external peripheral surface 491,501 of corresponding axis sealing 49,50 and respective aperture 47,48.The function of the peripheral wall 471,481 of this bearing jack 47,48 is as sealing surfaces.External peripheral surface 491,501 is relative with the sealing surface.
Shown in Fig. 3 (b), the first and second discharge pressure guiding channels 63,64 are formed on the chamber confining wall 143 of this rear case spare 14, and this chamber confining wall 143 has been determined the 5th pump chamber 43 of compression stage in the end.Shown in Fig. 4 (a), this first discharge pressure guiding channel 63 is connected on the region of maximum compression 432, and the volume of this compressing area changes along with the rotation of the 5th rotor 27,32, and this first discharge pressure guiding channel 63 also is connected on the through hole 141.Shown in Fig. 5 (a), this second discharge pressure guiding channel 64 is connected on region of maximum compression 432 and the through hole 142.
Shown in Fig. 1 (a), 4 (a) and 5 (a), one cooling annular chamber 65 is formed in this rear case spare 14, this cooling annular chamber 65 is around this shaft sealing 49,50, cooling liquid circulates in this annular chamber, cooling liquid in this annular chamber 65 makes the lubricant oil Y in bearing jack 47,48 cool off, and this has prevented this lubricant oil Y evaporation.
Shown in Fig. 1 (b), 6 (a) and 6 (b), one annular leakproof ring 66 is arranged on the small diameter portion 59 of this first shaft sealing 49 to stop flowing of oil, and this leakproof ring 66 comprises first stop part 67 with a minor diameter and has large diameter second stop part 68.One front end of this bearing support 45 has an annular protrusion 69 that inwardly stretches out, and annular first oil pocket 70 and annular second oil pocket 71 have been determined with respect to leakproof ring 66, this first oil pocket 70 is round this first stop part 67, and this second oil pocket 71 is round this second stop part 68.
This first oily stop part (oil stopper) 67 has the circumferential surface 671 of a taper, distance between the circumferential surface 671 of this taper and the axis 191 of first running shaft 19 increases corresponding to gear receiving cavity 331 1 sides from the side direction corresponding to the 5th pump chamber 43.
The circumferential surface 671 of this first stop part 67 is arranged in first oil pocket 70, and the circumferential surface 681 of this second stop part 68 is arranged in second oil pocket 71.This circumferential surface 671 is relative with the peripheral wall surface 702 that limits this first oil pocket 70, and the circumferential surface 681 of this second stop part 68 is relative with the peripheral wall surface 712 that limits this second oil pocket 71.
The rear surface 672 of this first stop part 67 is relative with the wall surface 701 that limits this first oil pocket 70, and the rear surface 682 of this second stop part 68 is arranged in Fig. 6 right side, and it is relative with the end face 711 that limits this second oil pocket 71.The rear surface 601 of the front surface 683 of this second stop part 68 and the large-diameter portion 60 of this first shaft sealing 49 is relative and far separate.
This rear surface 682 is perpendicular to the axis 191 of running shaft 19, and prevention oil is mobile.The circumferential surface 671 of this taper near a side place of gear receiving cavity 331 in abutting connection with the rear surface 682 location, position.The circumferential surface 671 of this taper is from the near-end 684 of this rear surface 682.Comprising the imaginary conical surfaces of circumferential surface 671 of this taper and the end face 701 of first oil pocket 70 intersects.
The large-diameter portion 60 of the 3rd stop part 72 and this first shaft sealing 49 forms.The 3rd annular oil cavity 73 is limited in first jack 47, around the 3rd stop part 72.One circumferential surface 721 of the 3rd stop part 72 is limited to a position that protrudes in the 3rd oil pocket 73.Simultaneously, the outer surface 721 of the 3rd stop part 72 is relative with the periphery wall surface 733 that limits the 3rd oil pocket 73.The rear surface 601 of the 3rd stop part 72 is relative with an end face 731 that limits the 3rd oil pocket 73 and in the position that is positioned at proximate end face 731, and a wall 732 of the front surface 722 of the 3rd stop part 72 and qualification the 3rd oil pocket 73 is relative and be positioned at the position of adjacent wall 732.
This stop part 67,68 and 72 radius reduce towards gear receiving cavity 331 gradually from the side corresponding to the 5th pump chamber 43.Equally, the radius of this oil pocket 70,71,73 also reduces towards gear receiving cavity 331 gradually from the side corresponding to the 5th pump chamber 43.This second stop part 68 is positioned at the position that is adjacent to first stop part 67 and than first stop part, 67 more close the 5th pump chambers 43.The radial center portion of the rear surface 682 of second stop part 68 is exposed in first oil pocket 70 corresponding to first stop part 67.The 3rd stop part 72 is positioned at the position that is adjacent to second stop part 68 and than second stop part, 68 more close the 5th pump chambers 43.The radial center portion of the rear surface 601 of the 3rd stop part 72 is exposed in second oil pocket 71 corresponding to second stop part 68.That is, the rear surface 682 of this second stop part 68 is the parts that limit the wall of first oil pocket 70.The rear surface 601 of the 3rd stop part 72 is the parts that limit the wall of second oil pocket 71.
One discharge passage 74 is limited in the end 144 of the lowest part of this first jack 47 and rear case spare 14, so that lubricant oil Y gets back to this gear receiving cavity 331.This discharge passage 74 has an axial part 741 and a radial part 742 that is formed on the end 144 that is formed on these hole 47 lowest parts, and this axial part 741 is connected with the 3rd oil pocket 73, and this radial part 742 is connected with gear receiving cavity 331.That is, the 3rd oil pocket 73 is connected with gear receiving cavity 331 by discharge passage 74.
Annular leakproof ring 66 is assemblied on the minor diameter 59 of second shaft sealing 50, to stop flowing of oil.The 3rd stop part 72 is limited on the large-diameter portion 80 of second shaft sealing 50.This first and second oil pocket 70,71 is limited in the bearing support 45, and the 3rd oil pocket 73 is limited in second hole 48.One discharge passage 74 is formed on the lowest part in this hole 48.Part corresponding to the 3rd oil pocket 73 of second shaft sealing 50 is connected with gear receiving cavity 331 by the discharge passage 74 corresponding to second shaft sealing 50.
The lubricant oil Y that is stored in the gear receiving cavity 331 is used for oilgear 34,35 and radial bearing 37.After lubricated radial bearing 37, lubricant oil Y enters into a through hole 691 of the projection 69 that is formed on each bearing support 45 by the gap 371,382 in each bearing 37.Then, this lubricant oil Y flows to corresponding first oil pocket 70 by the gap g1 between the end face 701 of the rear surface 672 of gap between the circumferential surface of the outer surface of the minor diameter 59 of this shaft sealing 49,50 and through hole 691 and corresponding first stop part 67 and corresponding first oil pocket 70.At this moment, the parts of lubricating oil Y that arrives the rear surface 672 of this first stop part 67 is thrown on all wall surfaces 702 or end face 701 of this first oil pocket 70 by the centrifugal force that is produced by the rotation of first stop part 67.At least a portion that is thrown among the lubricant oil Y on all wall surfaces 702 or the end face 701 remains on wall 702 or the surface 701.This remaining lubricant oil Y by its deadweight along wall 701,702 to dirty, and arrive the lowest part zone of this first oil pocket 70.After the lowest part zone that arrives this first oil pocket 70, this lubricant oil Y flows to the lowest part of second oil pocket 71.
After entering first oil pocket 70, the gap g2 that this lubricant oil Y passes through between the end face 711 of the rear surface 682 of this second stop part 68 and second oil pocket 71 flows to second oil pocket 71.At this moment, be thrown on all wall surfaces 712 or end face 711 of second oil pocket 71 by the centrifugal force that the rotation by second stop part 68 produces at the lubricant oil Y on the rear surface 682.At least a portion of getting rid of among the lubricant oil Y that delivers on all wall surfaces 712 or the end face 711 remains on all wall surfaces 712 or the surface 711.This remaining lubricant oil Y surfacewise 712,711 to dirty, and arrives the lowest part of this second oil pocket 71 by its deadweight.
After the lowest part that arrives second oil pocket 71, this lubricant oil Y flows to the lowest part of the 3rd oil pocket 73.
After entering second oil pocket 71, the gap g3 that this lubricant oil Y passes through between the end face 731 of the rear surface 601 of the 3rd stop part 72 and the 3rd oil pocket 73 flows to the 3rd oil pocket 73.At this moment, be thrown on all wall surfaces 733 or end face 731 of the 3rd oil pocket 73 by the centrifugal force that the rotation by the 3rd stop part 72 produces at the lubricant oil Y on the rear surface 601.At least a portion of getting rid of among the lubricant oil Y that delivers on all wall surfaces 733 or the end face 731 remains on this wall 733 or the surface 731.This remaining lubricant oil Y along this wall 733 and surfacewise 731 to dirty, and arrives the lowest part of the 3rd oil pocket 73 by its deadweight.
The lubricant oil of part got rid of the part of all wall surfaces 702 delivered on running shaft 19,20 or end face 701 from the rear surface 672 of first stop part 67 after, the lubricant oil of this part can drop onto on the outer surface 671 of taper.Equally, after being thrown to all wall surfaces 712 or end face 711 from rear surface 682, the lubricant oil Y of part also drops onto on the outer surface 671 of taper.After the outer surface 671 that drops onto taper, this lubricant oil Y gets rid of to periphery wall surface 702 by the centrifugal force that is produced by the rotation of leakproof ring 66 and send, or 671 moves from the side direction end face 701 corresponding to rear surface 682 surfacewise.When end face 701 moved, this lubricant oil Y was thrown to end face 701 or moves on the rear surface 672 of first stop part 67 on the outer surface 671 in taper.Therefore, behind the outer surface 671 that arrives taper, this lubricant oil Y moves to the lowest part of second oil pocket 71.
After the lowest part that arrives the 3rd oil pocket 73, this lubricant oil Y gets back in this gear receiving cavity 331 by corresponding discharge passage 74.
First embodiment has following advantage:
(1-1) when this vacuum pump operation, pressure in five pump chambers 39,40,41,42,43 is lower than the pressure in gear receiving cavity 331, wherein this gear receiving cavity 331 is zones that are exposed to atmospheric pressure, therefore, vaporific lubricant oil Y flows to the 5th pump chamber 43 along the surface of leakproof ring 66 and the surface of shaft sealing 49,50.In order to prevent that vaporific lubricant oil Y from entering into the 5th pump chamber 43, this lubricant oil Y preferably liquefies on a wall of fixing.Equally, at lubricant oil Y on this running shaft 19,20 or on the parts that rotate integratedly with this running shaft 19,20, preferably move to this fixed wall.
This stop part 67,68,72 moves to lubricant oil Y on the wall that limits this oil pocket 70,71,73 effectively, because the increase of the quantity of this stop part is used to receive the also increase to some extent of zone of oil in this stop part.Owing to be used to receive the increase in oily zone, the quantity of the oil that the centrifugal force that produces by the rotation by this stop part throws away also increases to some extent.In other words, this stop part 67,68,72 that is arranged on each running shaft 19,20 has stoped flowing of oil effectively.
(1-2) the lubricant oil Y on this stop part 67,68,72 gets rid of in the oil pocket 70,71,73 of this stop part 67,68,72, get rid of the lubricant oil Y in this oil pocket 70,71,73 and arrive on the wall of determining this oil pocket 70,71,73, at last, determine that at this lubricant oil Y on wall of oil pocket 70,71,73 arrives in this discharge passage 74.Because this stop part the 67,68, the 72nd, circumjacent by this oil pocket 70,71,73 respectively, the lubricant oil Y that is thrown away by this stop part 67,68,72 directs in this gear receiving cavity 331 at an easy rate.
(1-3) this vaporific lubricant oil Y moves from a side direction the 5th pump chamber 43 directions corresponding to gear receiving cavity 331 by this oil pocket, and the closure property of each oil pocket 70,71,73 is for preventing that this mist lubrication oil the mobile of Y from being very important.
First stop part 67 is positioned on the position than second stop part, 68 more close these gear receiving cavities 331, and the function of the rear surface 682 of this second stop part 68 is to limit this first oil pocket 70 corresponding to first stop part 67; Equally, second stop part 68 is positioned on the position than the 3rd stop part 72 more close these gear receiving cavities 331, and the function of the rear surface 601 of the 3rd stop part 72 is to limit this second oil pocket 71 corresponding to second stop part 68.This structure is independently of one another and be quite simple for the closure property that improves each oil pocket 70,71,73 for keeping this oil pocket 70,71,73.
(1-4) first and second oil pockets the 70, the 71st form with respect to the projection 69 of this bearing support 45 respectively, because this oil pocket 70,71 is formed in the bearing support 45 that supports this radial bearing 37, the sealability of this oil pocket 70,71 increases.
(1-5) when this vacuum pump operation, pressure in five pump chambers 39,40,41,42,43 is lower than the pressure in gear receiving cavity 331, wherein this gear receiving cavity 331 is zones that are exposed to atmospheric pressure, therefore, vaporific lubricant oil Y flows to the 5th pump chamber 43 along the surface of leakproof ring 66 and the surface of shaft sealing 49,50.The liquefaction of this vaporific lubricant oil Y in the passage of a bending is easier than the liquefaction in passage always, and in other words, when the wall of this vaporific lubricant oil Y and formation one bending channel collided, this mist lubrication oil Y was easy to liquefaction.This first stop part 67 has the tapered peripheral surface 671 that is arranged in first oil pocket 70, in first oil pocket 70 this vaporific lubricant oil Y be because first stop part 67 that is located in this first oil pocket 70 produces bending along the passage that moves; Second stop part 68 has the circumferential surface 681 that is located in this second oil pocket 71, in second oil pocket 71 this vaporific lubricant oil Y be because second stop part 68 that is located in this second oil pocket 71 produces bending along the passage that moves.
The 3rd stop part 72 has the circumferential surface 721 that is located in the 3rd oil pocket 73, in the 3rd oil pocket 73 this vaporific lubricant oil Y be because the 3rd stop part 72 that is located in the 3rd oil pocket 73 produces bending along the passage that moves.Because the tapered peripheral surface 671,681,721 of this stop part 67,68,72 lays respectively in this oil pocket 70,71,73, the mist lubrication oil Y in this oil pocket 70,71,73 can arrive in the 5th pump chamber 43 hardly.
(1-6) from the through hole 691 of each bearing support 45 at the rear surface 672 of first stop part 67 and the passage of the gap g1 this end face 701, its function is as from lead to the oil duct of this first oil pocket 70 corresponding to a side of gear receiving cavity 331, and this first stop part 67 makes and narrows down at the gap of this oil duct end g1.
From this first oil pocket 70 at the rear surface 682 of second stop part 68 and the passage of the gap g2 this end face 711, its function is as by this first oil pocket 70, from lead to the oil duct of this second oil pocket 70 corresponding to a side of gear receiving cavity 331, and this second stop part 68 makes and narrows down at the gap of this oil duct end g2.
From this second oil pocket 71 at the front surface 722 of the 3rd stop part 72 and the passage of the gap g3 this end face 731, its function is as by this first oil pocket 70 and second oil pocket 71, from lead to the oil duct of the 3rd oil pocket 73 corresponding to a side of gear receiving cavity 331, and the 3rd stop part 72 makes and narrows down at the gap of this oil duct end g3.
The end of this oil duct (gap g1, g2, g3) is very narrow, and this structure is preventing that mist lubrication oil Y from entering into each oil pocket the 70,71, the 73rd from the side corresponding to gear receiving cavity 331, and is favourable.
(1-7) this lubricant oil Y moves to the 5th pump chamber 43 directions along the surface of leakproof ring 66 and the surface of shaft sealing 49,50, lubricant oil on rear surface 682 radially throws away by the centrifugal force that the rotation by this leakproof ring 66 produces, and this lubricant oil is thrown on the circumferential surface 671 of this taper from this rear surface 682; The centrifugal force that produces by rotation to this lubricant oil of small part by this leakproof ring 66, from minor diameter one side direction major diameter one side shifting of the circumferential surface 671 of this taper.In other words, this lubricant oil Y moves to the direction away from the 5th pump chamber 43, and this is favourable preventing that oil from entering into the 5th pump chamber 43.That is, because the circumferential surface 671 of taper is adjacent to this rear surface 682, this oil pump Y can prevent that it from moving to the 5th pump chamber 43 directions.
(1-8) smallest diameter portion of this tapered peripheral surface 671 is directly connected on the most approaching end 684 of rear surface 682 of this second oily stop part 68, if being parallel to a circumferential surface of the axis of this running shaft 19,20 is connected on the most approaching end of this rear surface 682, the parts of lubricating oil Y that throws away from this rear surface 682 arrives on this circumferential surface, can get back at the lubricant oil on this circumferential surface on the rear surface 682 of this second stop part 68, this is favourable preventing that oil from entering into the 5th pump chamber 43.Yet in this first embodiment, the circumferential surface 671 of this taper is to be directly connected on the rear surface 682 of this second stop part 68, and this structure prevents to get back on this rear surface 682 from the lubricant oil Y that this rear surface 682 throws away.
(1-9) on the axis 191,201 of this running shaft 19,20, the circumferential surface 491 of lubricant oil Y along the front surface 492,502 of this shaft sealing 49,50 from shaft sealing 49,50 flows downward to the 5th pump chamber 43; Under the axis 191,201 of this running shaft 19,20, lubricant oil Y is upwards mobile to the 5th pump chamber 43 from the circumferential surface 491 of shaft sealing 49,50 along the front surface 492,502 of this shaft sealing 49,50.Therefore, this lubricant oil Y enters into the 5th pump chamber 43 along this shaft sealing 49,50 on axis 191,201.
The lubricant oil Y that is sent on the peripheral wall surface 702,712 to small part is retained on this peripheral wall surface 702,712.On running shaft 19,20, this peripheral wall surface the 702, the 712nd is from what have a down dip corresponding to a side direction of gear receiving cavity 331 corresponding to a side direction of the 5th pump chamber 43; That is, the lubricant oil Y edge on the part peripheral wall surface 702,712 on the running shaft 19,20 is mobile with respect to being directed downwards of running shaft 19,20, and flows to the direction away from the 5th pump chamber 43.Because this peripheral wall surface 702,712 allows this lubricant oil Y along mobile with respect to being directed downwards of running shaft 19,20, and flows to the direction away from the 5th pump chamber 43, has therefore prevented that effectively this lubricant oil Y from entering into the 5th pump chamber 43.
(1-10) the lubricant oil Y on the part peripheral wall surface 702,712 on the running shaft 19,20 flows downward along the wall 701,711 perpendicular to the axis 191,201 of this running shaft 19,20, after this, this lubricant oil Y flows down to the position that is lower than this running shaft 19,20 reposefully along this wall 701,711.Be connected in and, allow the lubricant oil Y in zone on this running shaft 19,20 to flow downward reposefully to the zone that is lower than this running shaft 19,20 perpendicular to the wall 701,711 on this peripheral wall surface 702,712.
(1-11) in the Roots pump 11 of running shaft 19,20 with cross setting, lubricant oil Y on these oil pocket 70,71,73 walls is flowed down in the 3rd oil pocket 73 by its deadweight, in other words, the lubricant oil Y on these oil pocket 70,71,73 walls is collected into the lowest part of the 3rd oil pocket 73 along this wall.Therefore, the lubricant oil on these oil pocket 70,71,73 walls flow in the gear receiving cavity 331 reliably by being connected in the discharge passage 74 on the 3rd oil pocket 73 lowest parts.
(1-12) be installed on the diameter of the diameter of the shaft sealing 49,50 on the running shaft 19,20 greater than the circumferential surface of running shaft 19,20.Therefore, the diameter of the labyrinth sealing 57,58 between the bottom surface 472,482 of the front surface 492,502 of shaft sealing 49,50 and bearing jack 47,48 is greater than the labyrinth sealed diameter between circumferential surface 192,202 that is located at running shaft 19,20 and the rear case spare 14.Because the diameter of labyrinth sealing 57,58 increases, therefore be used to prevent the also increase to some extent of volume in the chamber, labyrinth 551,552,561,562 of pressure surge, it has improved the sealability of labyrinth sealing 57,58.In other words, gap between the bottom surface 472,482 of the front surface 492,502 of each shaft sealing 49,50 and corresponding bearing jack 47,48 is suitable for keeping this labyrinth sealing 57,58 improving its sealability aspect the volume that increases chamber, labyrinth 551,552,561,562.
(1-13) because the gap between each bearing jack 47,48 and corresponding shaft sealing 49,50 reduces, for lubricant oil Y, the gap that enter between this bearing jack 47,48 and shaft sealing 49,50 is very difficult.This each have the bottom surface 472,482 in hole 47,48 of peripheral wall 471,481 and the end face 492,502 of corresponding shaft sealing 49,50 easily forms structure close to each other.Therefore, in the gap between the bottom of the top of each annular protrusion 53,54 and corresponding annular groove 55,56 and the gap between the front surface 492,502 of the bottom surface 472,482 of each jack 47,48 and corresponding shaft sealing 49,50 can easily reduce.Because reducing of gap, the sealability of this labyrinth sealing 57,58 increases, that is, the bottom surface 472,482 of each jack 47,48 is suitable for holding this labyrinth sealing 57,58.
(1-14) this labyrinth sealing 57,58 has stoped gas flow fully.When this Roots pump 11 starts, pressure in five pump chamber 39-43 is higher than atmospheric pressure, yet, each labyrinth sealing 57,58 prevents that gas from leaking into the gear receiving cavity 331 from the 5th pump chamber 43 along the surface of corresponding axis sealing 49,50, promptly, this labyrinth sealing 57,58 has prevented the oily leakage and the leakage of gas, and is best noncontact seal.
Though (1-15) As time goes on the sealability of noncontact seal can not reduce, this is different from the direct contact seal as lip-type seal, and the sealability of noncontact seal is lower than the sealability of direct contact seal.This stop part 67,68,72 has compensated sealing type energy, and each circumferential surface 671,681,721 lays respectively in this oil pocket 70,72,73, and this structure has further compensated its sealed type energy.
(1-16) circumferential surface 671 of this taper is adjacent to the rear surface 682 of second stop part 68, and this has further compensated its sealed type energy.
(1-17) because the rotation of first running shaft 19, lubricant oil Y in first spiral chute 61 is from corresponding to side directed corresponding to gear receiving cavity 331 of a side direction of the 5th pump chamber 43, and the lubricant oil Y in spiral chute 61 moves from the side direction gear receiving cavity 331 corresponding to the 5th pump chamber 43; Because the rotation of second running shaft 20, lubricant oil Y in second spiral chute 62 is from corresponding to side directed corresponding to gear receiving cavity 331 of a side direction of the 5th pump chamber 43, and the lubricant oil Y in spiral chute 62 moves from the side direction gear receiving cavity 331 corresponding to the 5th pump chamber 43.In other words, has the leakage that has fully prevented lubricant oil Y as the shaft sealing 49,50 of first and second spiral chutes 61,62 of pumping installations function.
It is consistent with the outer surface of the large-diameter portion 60 of first and second shaft sealings 49,50 (1-18) to be formed with the external peripheral surface 491,501 of spiral chute 61,62 on it, when shaft sealing 49,50 rotations, and the speed maximum of this part.Be located at the gas between the peripheral wall 471,481 of the external peripheral surface 491,501 of each shaft sealing 49,50 and corresponding bearing jack 47,48, by first and second spiral chutes 61,62 of this high speed rotating, effectively from corresponding to a thruster of the 5th pump chamber 43 to corresponding to gear receiving cavity 331 1 sides.Be located between the peripheral wall 471,481 of the external peripheral surface 491,501 of each shaft sealing 49,50 and corresponding bearing jack 47,48 this lubricant oil Y and effectively from flowing together to gas corresponding to gear receiving cavity 331 1 sides corresponding to 43 1 thrusters of the 5th pump chamber.Be formed on the spiral chute 61,62 on the external peripheral surface 491,501 of shaft sealing 49,50, prevented that effectively lubricant oil Y from by the gap between external peripheral surface 491,501 and the peripheral wall 471,481, leaking into the 5th pump chamber 43 from corresponding bearing jack 47,48.
(1-19) from moving corresponding to pump chamber 43 1 side direction gear receiving cavities 331 directions, this lubricant oil of part arrives the front surface 722 of the 3rd stop part 72 to this lubricant oil Y by this spiral chute 61,62.At this moment, the centrifugal force that the lubricant oil Y on this front surface 722 produces by the rotation by the 3rd stop part 72 is thrown toward the peripheral wall surface 733 of the 3rd oil pocket 73, and the lubricant oil Y that throws away to this peripheral wall surface 733 arrives on this peripheral wall surface 733.In other words, this lubricant oil Y by each spiral chute 61,62 from corresponding to the 5th pump chamber 43 1 side direction corresponding to gear receiving cavity 331 1 side shiftings, the 3rd stop part 72 directs into lubricant oil Y in the gear cavity 331 by the 3rd oil pocket 73 then.
(1-20) between the circumferential surface 192 of first running shaft 19 and through hole 141, have a little gap, between the chamber confining wall 143 of each rotor 27,32 and rear case spare 14, also have a little gap.Therefore, this labyrinth sealing 57 is exposed in the pressure of the 5th pump chamber of introducing by this long and narrow gap 43.Equally, have a little gap between the circumferential surface 202 of second running shaft 20 and through hole 142, therefore, this second labyrinth sealing 58 is exposed in the pressure of the 5th pump chamber 43 by this gap.If there is not passage 63,64, this labyrinth sealing 57,58 similarly is exposed in the pressure of suction area 431 and in the pressure of region of maximum compression 432.
The first and second discharge pressure guiding channels 63,64 make labyrinth sealing 57,58 be exposed in the pressure of region of maximum compression, promptly, this labyrinth sealing 57,58 is subjected to the influence of pressure in region of maximum compression by this guiding channel 63,64, greater than the influence that is subjected to pressure in suction area 431.Therefore, contrast does not form the situation of discharge pressure guiding channel 63,64, and the labyrinth sealing 57,58 among this first embodiment will be subjected to higher pressure; The result is, contrast does not form the situation of discharge pressure guiding channel 63,64, acting on the front surface of this labyrinth sealing 57,58 and the pressure difference on the rear surface reduces significantly, in other words, this discharge pressure guiding channel 63,64 has significantly improved the performance that labyrinth sealing 57,58 prevents leakage of oil.
(1-21) because this Roots pump 11 is dry types, do not use lubricant oil Y in five pump chambers 39,40,41,42,43, therefore, the present invention is suitable for Roots pump 11.
The present invention can also implement with other form, and for example, the present invention can implement with second to the 6th embodiment shown in Fig. 9 to 13 respectively.In second to the 6th embodiment, used similar or identical reference character with the assembly that corresponding assembly is similar or identical among first embodiment, because first and second running shafts 19,20 have identical structure, have only described first running shaft 19 in second to the 6th embodiment.
In second embodiment as shown in Figure 9, one groove 493 is formed in the large-diameter portion 60 of this shaft sealing 49, the circumferential surface 494 of this groove 493 is tapers, so that this groove 493 is from widening corresponding to the 5th pump chamber 43 1 side direction gear receiving cavities 331 directions, this discharge passage 74 is directed downwards inclination to gear receiving cavity 331.
Lubricant oil Y on this circumferential surface 494 moves to gear receiving cavity 331 directions by the centrifugal force that is produced by the rotation of this shaft sealing 49, and after this, this lubricant oil Y arrives on this end face 731; Then, this lubricant oil Y throws away to the peripheral wall surface 733 of the 3rd oil pocket 73.This groove 493 has reduced the weight of this shaft sealing 49, and this groove has also increased the quantity of the oil that this shaft sealing 49 is accepted before the 3rd oil pocket 73.
In the 3rd embodiment as shown in figure 10, a pair of leakproof ring 75,76 is arranged on the minor diameter 59 of this shaft sealing 49, and stripper loop 77,78 is arranged in the hole 47; This leakproof ring 75,76 has been determined three oil pockets 79,80,81 in the gap between the bottom surface 472 in the projection 69 of bearing support 45 and hole 47.
In the 4th embodiment as shown in figure 11, stop part 82,83,72 and this shaft sealing 49 form.
In the 5th embodiment as shown in figure 12, stop part 84,85,72 and this shaft sealing 49 form.The radial dimension of this stop part 84,85,72 increases in this order gradually, this stop part 84,85,72 respectively by oil pocket 86,87,88 round, the radius of oil pocket 86,87,88 also increases in this order gradually, and the peripheral wall 861,871,881 of this oil pocket 86,87,88 is not taper.The 5th embodiment has the identical advantage as (1-1) to (1-5), (1-8) to (1-14) and (1-15) to (1-20).
In the 6th embodiment as shown in figure 13, end face and this rotor 27 of one shaft sealing 49A and this running shaft 19 form, this shaft sealing 49A be arranged in be formed in the face of a hole 89, one labyrinth sealings 90 on the antetheca of the rear case spare 14 of rotor housing spare 12 between the bottom 891 in the rear surface of the first shaft sealing 49A and hole 89.
One leakproof ring 91,92 is arranged on the running shaft 19, and an annular oil cavity 93 is formed between the projection 69 of the bottom 472 in hole 47 and bearing support 45.
For a person skilled in the art, as can be seen: under the situation that does not break away from the spirit and scope of the present invention, the present invention can implement with other special form.Particularly, to implement with following form be understandable in the present invention.
(1) four or more stop part can be set along the axis of each running shaft.
(2) in first embodiment, each shaft sealing 49,50 can form with corresponding leakproof ring 66.
(3) in the 3rd embodiment, each Simmer ring 77,78 can form.
(4) the present invention can be applied in the vacuum pump of other type that is different from roots-type.
Therefore, it is exemplary rather than restrictive that these examples and embodiment only are considered to, the details that the invention is not restricted to provide herein, and can in the scope of accessory claim and equivalent scope, make amendment.

Claims (15)

1. vacuum pump sucks gas by means of this vacuum pump of rotation of running shaft (19,20) by the gas transfer body of handling in pump chamber (39-43) (23-32), it is characterized in that it comprises:
The housing member (14,33) that holds oil, the wherein said housing member (14,33) that holds oil limits an oil district (331) in abutting connection with described pump chamber (39-43), and described running shaft (19,20) has a lug boss, and this lug boss protrudes into the described oil district (331) from the housing member (14,33) of pump chamber (39-43) through holding oil; And
A plurality of stop parts (67,68,72; 84,85,72), described stop part is positioned on the described running shaft (19,20), rotating integratedly with running shaft (19,20), and prevents that oil from entering into described pump chamber (39-43), wherein said stop part (67,68,72; 84,, and arrange towards the order that You Qu (331) reduces gradually that from a side wherein each stop part (67,68,72 near pump chamber (39-43) by diameter 85,72) along the axially locating of described running shaft (19,20); 84,85,72) has an outer surface (671,681,721); And
A plurality of annular oil cavities (70,71,73; 79-81; 86-88), each annular oil cavity centers in the described outer surface, wherein said oil pocket (70,71,73; 79-81; 86-88) arrange towards the order that You Qu (331) reduces gradually from a side near pump chamber (39-43) by diameter.
2. pump as claimed in claim 1 is characterized in that, the paired stop part (67,68,72 of adjacency; 84, one 85,72) is first stop part (67) of distinguishing (331) near oil, and in the paired stop part another is second stop part (68) near this pump chamber (39-43), wherein this second stop part (68) has one perpendicular to the axis of running shaft (19,20) and in the face of the end face (682) in this oil district (331), and this end face (682) has a part, and this part is positioned near the radial center and is exposed to the residing oil pocket of this first stop part (70).
3. pump as claimed in claim 1 is characterized in that it also comprises: a discharge passage (74), this discharge route is connected to this oil district (331) with this oil pocket, oil is directed in this oil district (331).
4. pump as claimed in claim 3 is characterized in that, this discharge passage (74) is connected to the lowest part of described oil pocket.
5. pump as claimed in claim 4 is characterized in that, this discharge passage (74) is basic horizontal or downward-sloping towards You Qu (331).
6. pump as claimed in claim 5, it is characterized in that, it also comprises: a plurality of all wall surfaces (702,712,733), the centre of curvature of each all wall surface and described running shaft (19,20) centre of curvature unanimity, each all wall surface (702 wherein, 712,733) center on described stop part at running shaft (19,20) outer surface (671 on, 681,721) at least a portion of one in, and at least one described all wall surface (702,712,733) tilt, so that on this periphery wall surface and described running shaft (19,20) distance between reduces towards You Qu (331).
7. pump as claimed in claim 1 is characterized in that, each stop part (67,68,72; 84, a periphery 85,72) protrudes into corresponding oil pocket (70,71,73; 79-81; 86-88).
8. pump as claimed in claim 7 is characterized in that, this oil pocket (70,71,73; 79-81; 86-88) form a curved pathway, this path extends towards the side near this oil district (331) from the side near described pump chamber (39-43).
9. pump as claimed in claim 8, it is characterized in that, this bending channel has an oily passage (g1, g2, g3) that radially extends, wherein should connect each oil pocket (70,71,73) by oil passage (g1, g2, g3) to adjacency, and narrower along the axial described oily passage (g1, g2, g3) of described running shaft (19,20) than described oil pocket (70,71,73).
10. as any described pump among the claim 1-9, it is characterized in that, each stop part (67,68,72) has the end face (672,682,683,601,722) perpendicular to the axis of described running shaft (19,20), wherein taper outer surface (671) is positioned to around this running shaft (19,20), this taper outer surface is in abutting connection with the end face (682) of at least one stop part (68), and this taper outer surface is than more close this oil district (331) of this adjacent end face (682); And the diameter of this taper outer surface (671) is from increasing gradually towards this oil district (331) near this pump chamber (39-43) side.
11., it is characterized in that this oil district (331) holds a bearing (37) that rotatably supports described running shaft (19,20) as any described pump among the claim 1-9.
12., it is characterized in that it also comprises as any described pump among the claim 1-9:
Annular shaft sealing (49,50), this annular shaft sealing is positioned to around this lug boss, and to rotate integratedly with this running shaft (19,20), wherein this shaft sealing (49,50) is positioned to than described stop part (67,68,72; 84,85,72) more close described pump chamber (39-43) and have along first sealing of radially extending of this shaft sealing (49,50) and form surface (492,502);
Second sealing that is formed on this housing member (14,33) that holds oil forms surface (472,482), and wherein this second sealing forms that surface (472,482) forms surface (492,502) in the face of described first sealing and to form surface (492,502) substantially parallel with described first sealing; And
Be positioned at the noncontact seal (57,58,90) between this first and second sealing formation surface (492,502,472,482).
13., it is characterized in that it also comprises as any described pump among the claim 1-9:
Be positioned at the sealing surfaces (471,481) on this housing member that holds oil; With
Annular shaft sealing (49,50), this annular shaft sealing is positioned to around this lug boss, and to rotate integratedly with this running shaft (19,20), wherein this shaft sealing (49,50) is positioned to than described stop part (67,68,72; 84,85,72) more close described pump chamber (39-43), this shaft sealing (49,50) comprise be positioned at this shaft sealing (49,50) in the face of the lip-deep pumping installations of described sealing surfaces (471,481), it is directed to a side near this oil district (331) with oil from the side near this pump chamber (39-43) between the surface of this shaft sealing (49,50) and sealing surface (471,481).
14. as any described vacuum pump among the claim 1-9, it is characterized in that, this running shaft is in a plurality of parallel running shafts (19,20), gear mechanism (34,35) is interconnected with one another this running shaft (19,20), so that this running shaft (19,20) rotates integratedly, and this gear mechanism (34,35) is arranged in this oil district (331).
15. vacuum pump as claimed in claim 14, it is characterized in that, a plurality of rotors (23-32) form around each running shaft (19,20), so that each rotor (23-32) plays the effect of described gas transfer body, and the described rotor on running shaft engages with described rotor on another running shaft.
CNB021437874A 2002-09-30 2002-09-30 Leaking oil proof sturctrue for vacuum pump Expired - Fee Related CN1309961C (en)

Priority Applications (1)

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CNB021437874A CN1309961C (en) 2002-09-30 2002-09-30 Leaking oil proof sturctrue for vacuum pump

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Application Number Priority Date Filing Date Title
CNB021437874A CN1309961C (en) 2002-09-30 2002-09-30 Leaking oil proof sturctrue for vacuum pump

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CN1309961C true CN1309961C (en) 2007-04-11

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JP2020109319A (en) * 2018-12-28 2020-07-16 株式会社荏原製作所 Bearing device and vacuum pump device

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE68488C (en) * R. ROEDEL in Köln a. Rh., Waisenhausgasse Nr. 5 Leather drive belts made of parallel longitudinal strips held apart by spacers
JPH066950A (en) * 1992-06-19 1994-01-14 Matsushita Seiko Co Ltd Terminal block for terminating winding of motor stator
JPH07158571A (en) * 1993-12-08 1995-06-20 Nippondenso Co Ltd Scroll type compressor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE68488C (en) * R. ROEDEL in Köln a. Rh., Waisenhausgasse Nr. 5 Leather drive belts made of parallel longitudinal strips held apart by spacers
JPH066950A (en) * 1992-06-19 1994-01-14 Matsushita Seiko Co Ltd Terminal block for terminating winding of motor stator
JPH07158571A (en) * 1993-12-08 1995-06-20 Nippondenso Co Ltd Scroll type compressor

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