CN1409013A - Gas compressor - Google Patents
Gas compressor Download PDFInfo
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- CN1409013A CN1409013A CN02152917A CN02152917A CN1409013A CN 1409013 A CN1409013 A CN 1409013A CN 02152917 A CN02152917 A CN 02152917A CN 02152917 A CN02152917 A CN 02152917A CN 1409013 A CN1409013 A CN 1409013A
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- Prior art keywords
- oil
- chamber
- rotor shaft
- blade
- lateral mass
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C29/028—Means for improving or restricting lubricant flow
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C29/026—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
To abolish the O-ring for sealing the space on the rotor shaft rear end surface side. There are provided at the ends of a tubular cylinder a front side block and a rear side block, and a rotor rotatable by a rotor shaft is arranged in a cylinder, there being formed in the rotor vane grooves in which vanes are accommodated so as to be capable of advancing and retreating and vane back pressure chambers, there being further provided a high pressure chamber and an oil sump portion, a lubricant oil space being provided in the rear side block and on the rear end surface side of the rotor shaft, there being provided an oil supply passage for supplying oil to the lubricant oil space from the oil sump portion, there being provided in the rear side block or in the rotor shaft a vane back pressure chamber oil passage 40 whose one end communicates with the oil accommodating space and whose other end communicates with the vane back chambers. The space on the rotor shaft rear end surface side can be formed solely by the rear side block, and the O-ring for sealing the high pressure chamber is abolished to thereby achieve an improvement in reliability. Due to the abolishment of the O-ring, it is also possible to achieve a reduction in cost and assembly man-hour.
Description
Technical field
The present invention relates to the gas compressor of use in vehicle or the like, wherein gas compressor is as parts of air conditioner.
Background technique
The gas compressor of vane type is known to be used in air conditioner, refrigerator or the like.Such gas compressor will be described with reference to figure 4.
A sidepiece at housing 1 has formed aspirating chamber 2, and contiguous aspirating chamber 2 provides the gas compression part.In gas compression part, tubular active chamber 3 is provided, on the longitudinal component of direction perpendicular to axial direction, have and enclose the surface in fact oval-shaped, and preceding lateral mass 4 and back lateral mass 5 be fixed on its axial end surface, thus parallel to each other.
As shown in Figure 5, in active chamber 3, arranged rotating rotor 6, supported by rotor shaft 10.In this rotor 6, formed a plurality of blade grooves 7 radially, and blade 8 is assembled to slidably in each blade groove 7, and remains in the blade groove 7.Further, in blade groove 7, enclose the end portion of side, form blade backpressure chamber 9, is communicated with, and oil is provided in the blade backpressure chamber, and auxiliary blade 8 is mobile forward or backward with groove.
Further, as shown in Figure 4, cyclone separator piece 14 is connected to the rear end of back lateral mass 5, be used for from the composition of the cooling gas separating oil of compression, and hyperbaric chamber 15 is formed on the rear end of back lateral mass 5 and cyclone separator piece 14.Housing 1 is formed with the release portion (not shown), thereby be communicated with hyperbaric chamber 15, and 15 bottom in the hyperbaric chamber, oil groove part 17 is provided, the cooling gas of compression discharges in hyperbaric chamber 15 by back lateral mass 5 and cyclone separator piece 14 in active chamber 3, and the high pressure cooling gas that discharges in hyperbaric chamber 15 is provided to the outside by liberation port.Further, separating the oil that obtains by cyclone separator piece 14 drops on the oil groove part 17.
Oil in the oil groove part 17 is in the effect of high pressure cooling gas release pressure, its mesohigh cooling gas is discharged in the hyperbaric chamber 15, and lubricant oil is from oil groove part 17, by being formed on the oil supply gallery 20,21 and 22 in active chamber 3, preceding lateral mass 4 and the back lateral mass 5 separately, be provided to the sliding bearing part of rotor shaft 10, come the lubrication sliding bearing part.Further, in the oil of the sliding bearing that offers rotor shaft 10 anterior ends and rear end, some offers the little space 30 that rear end is surperficial and cyclone separator piece 14 forms by rotor shaft 10, the rear end surface that is used to prevent to block rotor shaft.Offer the oil in this little space 30, space after passing between the anterior end surface of the rear end of lateral mass 5 surface and cyclone separator piece 14, and further be passed in the lateral mass 5 of back and form oil supply gallery 23, and offer a plane groove 26, thereby be blade backpressure chamber 9 fuel feeding.
As mentioned above, by back lateral mass 6 and cyclone separator piece 14, form the little space 30 of rotor shaft rear end surface portion, thereby cut little space 30 the release pressure space outside cyclone separator piece 14, arrange O type ring 31, be used for sealing between back lateral mass 6 and cyclone separator piece 14, thereby surround little space 30.
Yet the space of rotor shaft rear end surface portion is filled with the oil of high temperature, and in the release pressure space outside the cyclone separator piece, have the gas or the oil of High Temperature High Pressure, thereby O type ring is owing to high temperature wears out, thereby can't keep suitable blade backpressure, and this is disadvantageous.
Summary of the invention
Considered that the problems referred to above obtain the present invention.The purpose of this invention is to provide compressor, wherein needn't center on little space mounting O type ring, avoided thus owing to the aging problem that causes of O type ring.
According to the present invention, in order to address the above problem, gas compressor comprises the tubular active chamber; Before lateral mass and back lateral mass, be positioned at the axial end of active chamber; Rotor is arranged in the active chamber rotationally; The blade groove is provided in the rotor; The blade backpressure chamber and is enclosed the side end portion and is communicated with in the blade groove; Rotor shaft is used for rotary rotor; The hyperbaric chamber, wherein pressurized gas is discharged into the hyperbaric chamber from active chamber inside; With the oil groove part, wherein storage is oily, and the force applications in hyperbaric chamber is on it, and the characteristics of gas compressor are that end surface one side provides the lubricant oil space in the lateral mass of back and behind the rotor shaft, and oil supply gallery is provided, be used for providing oil to lubricated space from the oil groove part, formed blade backpressure chamber oil supply gallery in back lateral mass or rotor shaft, end of passage is communicated with oil storage space, and another end is communicated with the blade backpressure chamber.
According to the present invention, the characteristics of gas compressor are to provide plane groove in the anterior end surface of back lateral mass, are communicated with the blade backpressure chamber, and are that plane groove is connected on the oil supply gallery, are connected thereby set up between oil supply gallery and blade backpressure chamber.
According to the present invention, the characteristics of gas compressor are, the blade backpressure chamber is formed in the rotor shaft along axial direction, and be that oil supply gallery is in the radial deflection of active chamber one side, and be communicated with the blade backpressure chamber, in oil supply gallery, arranged throttle valve,, limited the area of opening of oil supply gallery by the power that produces in the oil supply gallery to the oil pumping of blade backpressure chamber.
Just, according to the present invention, form little space between the rear end of rotor shaft and the back lateral mass, and be provided to the oil in the little space, the oil supply gallery by forming in back lateral mass or the rotor shaft is provided in the blade backpressure chamber, thereby can not use any O type ring, from the hyperbaric chamber, cut little space, can cancel O type ring like this, and at suitable pressures oil is provided in the blade backpressure chamber.
Above-mentioned oil supply gallery can be formed in the lateral mass of back, and partly is communicated with plane groove etc. like this.Can also in rotor shaft, extend along axial direction, oil supply gallery is provided, thus with little spatial communication, and make it backward during the lateral mass intrinsic deflection, be connected on the part such as plane groove.
The blade backpressure asphalt channel is formed in the rotor shaft, thereby extend along axial direction, and oil supply gallery is sidelong at active chamber one and is penetrated ground deflection, and be communicated with the blade backpressure chamber, in this structure, rotating speed increase along with rotor shaft, centrifugal force along radial direction effect in the oil supply gallery part increases, and in oil supply gallery, promote the power that oil moves to peripheral side, just, the power to the oil pumping of blade backpressure chamber acts in the oil in the rotor shaft tempestuously, thereby have such danger, promptly from the lubricant oil space of rotor shaft rear end one side, extracted excessive oil out.For this reason, desired as claim 3, can in oil supply gallery, arrange throttle valve, by the power that produces in the oil supply gallery to the oil pumping of active chamber one side, limit the opening area of oil supply gallery, can prevent that thus excessive draft is applied in the lubricant oil space, thereby can guarantee the lubricant oil of appropriate amount.
Description of drawings
Fig. 1 is the summary positive view according to the gas compressor of first embodiment of the invention.
Fig. 2 is the summary positive view according to the gas compressor of second embodiment of the invention.
Fig. 3 is according to the amplification view of third embodiment of the invention around the part of blade backpressure chamber.
Fig. 4 is the summary positive view of existing gas compressor.
Fig. 5 is its sectional view, has shown active chamber and inside thereof.
Embodiment
(first embodiment)
With reference now to accompanying drawing, the first embodiment of the present invention is described.With those identical parts in the prior art example, by identical reference number indication, and the description of parts is omitted or deletes as required like this.
Fig. 1 has shown the schematic configuration of gas compressor.Gas compressor comprises: housing 1 has the part of bleeding (not shown) and release portion (not shown) at an end.The exhaust tube (not shown) is connected on the part of bleeding, and is used for from the outside cooling gas suction with compression, and the releasing tube (not shown) is connected on the release portion, be used for will compression refrigerant offer condenser or similar (not shown).
In 1 one sidepieces of housing (bleeding point one side), aspirating chamber 2 is provided, it is communicated with bleeding point.Further, the middle part in housing 1, arranged: tubular active chamber 3, it has on the longitudinal profile of direction perpendicular to axial direction encloses the surface in fact oval-shaped; Before lateral mass 4 (bleeding point one side), be fixed to the axial end surface of active chamber 3, thus parallel to each other; With back lateral mass 5 (liberation port one side).
Yet, as shown in Figure 5, in active chamber 3, arranged rotating rotor 6, support by rotor shaft 10, and this rotor 6 has a plurality of blade grooves 7 that radially form, blade 8 is assembled in each of these grooves slidably, and remains in wherein.Further, form blade backpressure chamber 9, thus with each blade groove 7 in enclose side end portion be communicated with.
In active chamber 3, the opening (not shown) is provided at preceding lateral mass 3 one sides, thereby is communicated with pressing chamber 3a, and the release aperture (not shown) is formed on back lateral mass 5 one sides; The gas that enters pressing chamber 3a by opening is compressed, and the pressurized gas that compresses in pressing chamber 3a, is discharged in the hyperbaric chamber 15 by the passage (not shown) that forms in release and the back lateral mass 5.Cyclone separator piece 141 is installed in rear end one side of back lateral mass 5, and in this cyclone separator piece 141, oil component is separated from pressurized gas.In the housing 1 after in back lateral mass 6 and cyclone separator piece 141, form hyperbaric chamber 15, and liberation port is formed in the housing 1, thereby is communicated with hyperbaric chamber 15.Further, 15 bottom provides oil groove part 17 in the hyperbaric chamber.
In the lateral mass 5 of back, form oil supply gallery 20, make the oil motion in the oil groove part 17, thus the axle center of rotor shaft 10 rear end that directly oil led, thus oil can offer the sliding bearing part of rotor shaft 10 rear end.Further, at certain mid point, oil supply gallery 20 is communicated with the oil supply gallery 21 that forms in active chamber 3 along axial direction, and oil supply gallery 21 is communicated with the oil supply gallery 22 of formation in the preceding lateral mass 4.Oil supply gallery 22 can offer oil rotor shaft 10 anterior terminal sliding bearing parts to anterior terminal extension of rotor shaft 10.Further, the anterior end surface of the rear end surface of lateral mass 4 and back lateral mass 5 before plane groove 25 and 26 is formed on separately, wherein preceding lateral mass 4 keeps contacting with rotor shaft 10; Offer the oil of rotor shaft 10 sliding bearings part, flow in the plane groove 25 and 26, and oil offers blade backpressure chamber 9.Further, in the lateral mass 5 of back, raised structures 10 is formed on the rear side end surface of rotor shaft 10, thereby forms the little space 35 of lubricant oil, and depression is provided at its inner surface.Just, little space is formed on the inside of back lateral mass 5.Form blade backpressure chamber asphalt channel 40 in the lateral mass 5 of back, wherein blade backpressure chamber asphalt channel 40 end is communicated with the little space 35 of lubricant oil, thereby blade backpressure chamber asphalt channel 40 extends along axial direction obliquely and in fact; Another end of blade backpressure passage 40 is connected in the plane groove 26, and is communicated with blade backpressure chamber 9.
The operation of above-mentioned gas compressor will be described below.
When making rotor 6 rotations by magnetic clutch 11 rotary rotor axles 10, because being provided in the blade backpressure chamber 9, centrifugal force and hydraulic oil (specifically describes below), applied extruding force to the periphery by rotating to blade.The blade 8 that has applied extruding force rotates, and keeps simultaneously closely contacting with the sidewall of preceding lateral mass 4 with back lateral mass 5 with the interior leg of active chamber 3.As the result of this rotation, produce draft, and cooling gas is passed through bleeding point suction housing 1 from the outside to active chamber inside.Cooling gas suction aspirating chamber 2, and by opening (not shown) suction active chamber 3.In active chamber 3, rotate the pressing chamber 3a that forms continuously by rotor 6 and blade 8, and continuous compression refrigeration gas.
The cooling gas of compression is discharged in the pressurized gas passage (not shown) of back lateral mass 5 formation from the release opening (not shown) that active chamber 3 forms.The pressurized gas that discharges is by the continuous motion of pressurized gas passage, and in cyclone separator piece 141, before pressurized gas was discharged into hyperbaric chamber 15, oil was therefrom separated.Be discharged into the pressurized gas in the hyperbaric chamber 15, by the liberation port of housing 1, from hyperbaric chamber 15, be discharged into continuously the external condensation device or similar in.On the other hand, the oil of separation falls into oil groove part 17.In oil groove part 17, because the pressure reduction between hyperbaric chamber 15 and the aspirating chamber 2, lubricant oil is provided to oil supply gallery 20, and offers the sliding bearing part of rotor shaft 10 rear end, and makes sliding bearing partly lubricated.Further, a part of oil in the oil supply gallery 20 flows to the asphalt channel 21 of active chamber 3, and passes through the asphalt channel 22 of preceding lateral mass 4, offers the sliding bearing part of rotor shaft 10 front side end, and makes sliding bearing lubricating.Then, offer the oil of the sliding bearing part of rotor shaft 10 front and rear ends, when passing the sliding bearing part, reduced pressure by throttling, offer blade backpressure chamber 9 by pair of planar groove 25 and 26 then, before wherein this is provided at plane groove 25 and 26 in the rotor one side end surface of lateral mass 4 and back lateral mass 5, helps blade 8 and advance or retreat.
Further, offer the oil of the sliding bearing part of rotor shaft rear end, partly travel forward, offer plane groove 26 as mentioned above, and partly motion backward, thereby offer rotor shaft 10 rear end surfaces and the little space 35 that cyclone separator piece 14 forms, prevent that rotor shaft rear end surface from blocking.The oil that offers this little space 35 passes blade backpressure chamber asphalt channel 40, and offers plane groove 26, and oil is offered blade backpressure chamber 9.
Be transported to the part oil of blade backpressure chamber 9 by sliding bearing part and asphalt channel 40, from blade backpressure chamber 9, leak, and be transported to the gap between rotor 6 and preceding lateral mass 4 or the back lateral mass 5, enclose the gap between the surface in blade 8 and the active chamber 3, and the gap between blade 8 and preceding lateral mass 4 or the back lateral mass 5, prevent wearing and tearing thus, and effectively seal by oil film.
In the above embodiments, because the raised structures of back lateral mass 5,15 have cut the little space 35 that holds oil on rotor shaft rear end surface from the hyperbaric chamber, thereby do not need to realize cutting by O type ring of the prior art.Like this, avoided because the aging problem that produces of O type ring.
(second embodiment)
Below with reference to Fig. 2 second embodiment is described.
In this embodiment, blade backpressure chamber asphalt channel is formed in the rotor shaft, allows the lip-deep little space of rotor shaft rear end to be communicated with plane groove.The description of such parts will be omitted or simplify to those parts identical with the prior art example with first embodiment by identical reference number indication, and.
As among first embodiment, in this embodiment, the position after rotor shaft 10 rear end surfaces provides raised structures in the lateral mass 5 of back, and little space 36 is formed between the internal surface of rotor shaft 10 rear end surface and back lateral mass 5.Further, rear end one side at rotor shaft 10 has formed blade backpressure asphalt channel 41 in the axle center, extends along axial direction, and the one end is formed in the little space 36.In asphalt channel 41 another terminal sides, asphalt channel 41 radial deflection before rotor shaft 6 side end surface, and to the periphery extension that is connected on the plane groove 26.
As among first embodiment, in this second embodiment, gas is compressed, and the gas of compression discharges from liberation port.Further, the oil in the oil groove part 17 offers the sliding bearing part of rotor shaft 10, as first embodiment, comes the lubrication sliding bearing part.Then, part oil offers the little space 36 of rotor shaft rear end surface one side, prevents that rotor shaft 10 rear end surfaces from blocking.The oil that offers little space 36 moves in rotor shaft 10 by asphalt channel, and in the radial deflection of rotor shaft 6 one sides, and offer plane groove 26, thus oil is offered the blade backpressure chamber.Equally in this embodiment, the lip-deep little space of rotor shaft rear end 15 cuts from the hyperbaric chamber by the protruding part of back lateral mass, thereby does not need to provide O type ring, and this mode can prevent because the aging problem that causes of O type ring.Further, in this embodiment, asphalt channel 41 is provided in the rotor shaft 10, thereby does not need fixedly thick wall part and form passage in back lateral mass 5 one sides, and has reduced the wall thickness, size etc. of protruding part, has reduced the volume of back lateral mass thus.As a result, can increase the volume in hyperbaric chamber.
In the preceding lateral mass 4 and back lateral mass 5 of this gas compressor, used sliding bearing at the bearing part of rotor shaft 10.Compare with the bearing hole situation of ball bearing or needle bearing, the hole that forms sliding bearing needs more high-precision polishing processing.Here, the term precision is meant, for example out of roundness in hole and cylindricity, the surface roughness of its internal surface etc.For the hole of highi degree of accuracy polishing, adding the smear metal and the broken end that produce man-hour is an important problem.
In the back lateral mass 5 of the gas compressor of the prior art that Fig. 4 shows, bearing hole is a through hole.The smear metal and the broken end that produce during this through hole of polishing processing can easily be discharged to outside the hole.Like this, in fact smear metal and broken end do not influence the polishing precision in hole.
On the contrary, in the back lateral mass 5 of the gas compressor of the present invention that Fig. 1 and 2 shows, this bearing hole is a blind hole.Under the situation of blind hole, polishing adds the smear metal and the broken end that produce man-hour and is not easy to discharge from the hole, and the identical processing method can not be by the processing through hole time realizes high-precision processing.For this reason, usual way is hocket process step and chip removal step, spend the plenty of time like this to polish the hole accurately, and smear metal and broken end does not have any influence.
In order to prevent to increase the required time of polishing processing, under the situation of the back lateral mass 5 in embodiment 1, the hole of asphalt channel 40 forms by processing in advance, thereby the smear metal and the broken end that produce during the polishing bearing hole can discharge by the hole of asphalt channel 40.
Under the situation of embodiment 2 back lateral mass 5, in the cutting tool in polishing machining bearing hole and abrasive tool, provide the hole, and smear metal and broken end are discharged by these holes.
(the 3rd embodiment)
In the 3rd embodiment, improved second embodiment, wherein the asphalt channel in second enforcement is formed in the rotor shaft.
Just, as in a second embodiment, the axial centre in rotor shaft 10 forms blade backpressure chamber asphalt channel 43, thereby extends along axial direction, and in the peripheral radial deflection of rotor 6 one side direction.Just, asphalt channel comprises shaft portion 42a and radius part 42b.
Further, in the attachment portion that is connected to radius part 42b, when axial component 42a when rotor one side is extended, axial component 42a reduces on diameter step by step; In the attachment portion, helical spring 45 is arranged on the radius part 42b, thereby extends back along axial direction, and ball valve body 46 is fixed to its rear portion end portion.When helical spring 45 does not carry, this valve body 46 be positioned at axial component 42a than the major diameter part, and guarantee big opening area at axial component 42a.On the other hand, under the state that helical spring 45 shrinks, valve body moves to the little side of axial component 42a diameter, and closes the opening of axial component 42a.In addition, this embodiment's structure is identical with second embodiment's, and the descriptions thereof are omitted.
In this 3rd embodiment, when compressor operation, gas is compressed, and lubricant oil moves in compressor; As in the above embodiments, oil moves along asphalt channel 42, and oil is offered blade backpressure chamber (not shown) from axial component 42a by radius part 42b.In this asphalt channel 42, by the rotation of rotor shaft 10, centrifugal action is on the oil of radius part 42b, and wherein oil moves in this passage, and the oil that moves in axial component 42a is to rotor one side suction.When the rotating speed of rotor shaft 10 increased, the centrifugal force and the suction power that act on the oil increased, and wherein oil moves in axial component 42a; Because this suction power, valve body 46 is to rotor one side shifting, and compression helical spring 45, and the opening of axial component 42 narrows down, restriction oil moves in axial component 42a, when the rotating speed of rotor shaft 10 increases, can prevent that oil is from the space of rotor shaft rear end one side thus, flow into too much in the blade backpressure chamber, guarantee the oil of appropriate amount like this in rotor shaft rear end surface one side.
As mentioned above, the invention provides gas compressor, comprise the tubular active chamber; Before lateral mass and Hou lateral mass, be positioned at the axial end of active chamber; Rotor is arranged in the active chamber rotationally; The blade groove is provided in the rotor; The blade backpressure chamber, be used for the blade groove in enclose the side end portion and be communicated with; Blade is contained in the blade groove, thereby can advance or retreat; Rotor shaft is used for rotary rotor; The hyperbaric chamber, wherein pressurized gas is discharged into the hyperbaric chamber from active chamber inside; With the oil groove part, wherein storage is oily, and the pressure effect in hyperbaric chamber wherein, and rear end surface one side with rotor shaft 10 in the lateral mass of back provides the lubricant oil space, oil supply gallery is provided, oil is partly offered the lubricant oil space from oil groove, and in back lateral mass or rotor shaft, form blade backpressure chamber asphalt channel, the one end is communicated with oil storage space, the other end of asphalt channel is communicated with the blade backpressure chamber, thus can be only by the back lateral mass, and one side forms the space on rotor shaft rear end surface, and omitted the O type ring of sealed high pressure chamber, improved reliability thus.Further, owing to omitted O type ring, can realize that cost reduces and assemble the minimizing in man-hour.
Claims (3)
1. gas compressor comprises:
Active chamber;
Before lateral mass and Hou lateral mass, be positioned at the axial end of active chamber;
Rotor is arranged in the active chamber rotationally;
The blade groove is arranged in the rotor;
The blade backpressure chamber, be arranged on the blade groove in enclose side;
Blade is contained in the blade groove, thereby can advance or retreat;
Rotor shaft is used for rotary rotor;
The hyperbaric chamber, wherein pressurized gas is discharged in the hyperbaric chamber from active chamber;
The oil groove part, wherein storage is oily, and the pressure effect in hyperbaric chamber is wherein;
The lubricant oil space is arranged in the lateral mass of back and the surperficial side of the rear end of rotor shaft;
Oil supply gallery is used for oil is partly offered the lubricant oil space from oil groove; With
Asphalt channel is formed in back lateral mass or the rotor shaft, an end of asphalt channel and lubricant oil spatial communication, and the other end is communicated with the blade backpressure chamber.
2. according to the gas compressor of claim 1, it is characterized in that forming plane groove in the anterior end surface of back lateral mass, be communicated with the blade backpressure chamber, and plane groove is connected on the asphalt channel, and between asphalt channel and blade backpressure chamber, is communicated with.
3. according to the gas compressor of claim 1, it is characterized in that in rotor shaft, forming the blade backpressure chamber along axial direction, and asphalt channel is in active chamber one side radial deflection, and be communicated with the blade backpressure chamber, in asphalt channel, arranged throttle valve, by the power that produces in the asphalt channel to the oil pumping of blade backpressure chamber, the opening area of restriction asphalt channel.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP307281/2001 | 2001-10-03 | ||
| JP2001307281A JP2003113787A (en) | 2001-10-03 | 2001-10-03 | Gas compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1409013A true CN1409013A (en) | 2003-04-09 |
Family
ID=19126771
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN02152917A Pending CN1409013A (en) | 2001-10-03 | 2002-10-03 | Gas compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20030063991A1 (en) |
| EP (1) | EP1300593A3 (en) |
| JP (1) | JP2003113787A (en) |
| CN (1) | CN1409013A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103382937A (en) * | 2012-05-03 | 2013-11-06 | Zf操作系统有限公司 | Positive displacement pump |
| CN105899810A (en) * | 2014-01-09 | 2016-08-24 | 康奈可关精株式会社 | Gas compressor |
| CN106481555A (en) * | 2015-08-25 | 2017-03-08 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of horizontal compressor and temperature equipment |
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| AU2004247229B2 (en) * | 2003-06-09 | 2006-12-14 | Saint-Gobain Ceramics & Plastics, Inc. | Fused zirconia-based solid oxide fuel cell |
| US9185538B2 (en) * | 2005-05-31 | 2015-11-10 | Qualcomm Incorporated | Wireless subscriber application and content distribution and differentiated pricing |
| JP5949386B2 (en) * | 2012-09-24 | 2016-07-06 | 株式会社豊田自動織機 | Vane type compressor |
| JP6171482B2 (en) * | 2013-03-28 | 2017-08-02 | 株式会社豊田自動織機 | Vane type compressor |
| ES2612232T3 (en) * | 2014-06-05 | 2017-05-12 | Wabco Europe Bvba | Vacuum pump and system of a vacuum pump and an engine |
| JP6350294B2 (en) * | 2015-01-15 | 2018-07-04 | 株式会社デンソー | Fuel pump |
| DE102016211913A1 (en) * | 2016-06-30 | 2018-01-18 | Schwäbische Hüttenwerke Automotive GmbH | Vane pump with pressurizable underwing area |
| KR102180179B1 (en) * | 2018-11-09 | 2020-11-18 | 엘지전자 주식회사 | Vain rotary compressor |
| CN113978206B (en) * | 2021-11-15 | 2023-07-21 | 常州康普瑞汽车空调有限公司 | Front cyclone blade type automobile air conditioner compressor |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS609436Y2 (en) * | 1976-05-15 | 1985-04-03 | 株式会社ボッシュオートモーティブ システム | Movable vane rotary compressor |
| JPS5874890A (en) * | 1981-10-30 | 1983-05-06 | Hitachi Ltd | Rotary vane compressor |
| US4507065A (en) * | 1982-05-13 | 1985-03-26 | Diesel Kiki Co., Ltd. | Vane compressor having drive shaft journalled by roller bearings |
| JPS60132086A (en) * | 1983-12-19 | 1985-07-13 | Toyoda Autom Loom Works Ltd | Sliding vane compressor |
| JPS60192891A (en) * | 1984-03-14 | 1985-10-01 | Hitachi Ltd | vane compressor |
| JP2840818B2 (en) * | 1995-08-31 | 1998-12-24 | セイコー精機株式会社 | Gas compressor |
-
2001
- 2001-10-03 JP JP2001307281A patent/JP2003113787A/en active Pending
-
2002
- 2002-09-30 US US10/261,635 patent/US20030063991A1/en not_active Abandoned
- 2002-10-01 EP EP02256837A patent/EP1300593A3/en not_active Withdrawn
- 2002-10-03 CN CN02152917A patent/CN1409013A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103382937A (en) * | 2012-05-03 | 2013-11-06 | Zf操作系统有限公司 | Positive displacement pump |
| CN105899810A (en) * | 2014-01-09 | 2016-08-24 | 康奈可关精株式会社 | Gas compressor |
| CN106481555A (en) * | 2015-08-25 | 2017-03-08 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of horizontal compressor and temperature equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2003113787A (en) | 2003-04-18 |
| EP1300593A2 (en) | 2003-04-09 |
| EP1300593A3 (en) | 2003-04-16 |
| US20030063991A1 (en) | 2003-04-03 |
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