CN104074760A - Rotary blade-type compressor - Google Patents
Rotary blade-type compressor Download PDFInfo
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- CN104074760A CN104074760A CN201410111444.2A CN201410111444A CN104074760A CN 104074760 A CN104074760 A CN 104074760A CN 201410111444 A CN201410111444 A CN 201410111444A CN 104074760 A CN104074760 A CN 104074760A
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Abstract
The invention discloses a rotary blade-type compressor comprising a back pressure application mechanism, which is provided with an upstream channel, a communicating chamber, a rotary channel,and a downstream channel. The upstream channel is disposed in the rear side plate, and is extended from the carrying surface of the rear side plate from an exhaust chamber. The communicating chamber is adjacent to the rear end of a rotary shaft body. The rotary channel is extended through the rotary shaft body, and can reach the peripheral surface of the rotary shaft body. The downstream channel is disposed in the rear side plate, and allows the communication between the communicating chamber and a back pressure chamber of a compression chamber in a compressed state. The upstream channel is intermittently communicated with the communicating chamber by the opening of the rear side plate and the opening of the rotary shaft body.
Description
Technical field
The present invention relates to a kind of rotary vane compressor.
Background technique
The open No.2012-127335 of Japanese unexamined patent application discloses a kind of rotary vane compressor, and it comprises housing, front side plate, back side panel, running shaft, rotor and multiple blade.
Housing has rotor chamber, suction chamber and discharge chamber.Rotor chamber is closed and is closed by back side panel in its back-end by front side plate at its front end.Running shaft is rotatably supported in housing.
Rotor arrangements in rotor chamber and can with rotor shaft synchronous rotary.Rotor has multiple radially extended blade grooves.In respective leaves film trap, receive slidably multiple blades.The rear surface of the internal surface of rotor chamber, the outer surface of rotor, front side plate, the front surface of back side panel and blade are combined the multiple pressing chambers of formation.Between blade bottom and blade groove, be formed with respectively multiple back pressure chambers.
Rotary vane compressor does not have sliding bearing (plain bearing) between running shaft and back side panel.But back side panel has cylindrical supporting plane and the supporting rotating shaft relative with the circumferential surface of running shaft.
When the pressing chamber being associated of each back pressure chamber is during in compression stage, each back pressure chamber is communicated with discharge chamber by back pressure applying mechanism.Back pressure applying mechanism comprises communication chamber, upstream passageway, rotating channel and downstream passage.The rear end of communication chamber and running shaft is adjacent to form.Upstream passageway is formed in back side panel and from discharge chamber and extends to communication chamber.Rotating channel is formed in running shaft, and rotating channel extends to the circumferential surface of running shaft and has opening at circumferential surface from communication chamber.The second channel that downstream passage is formed in back side panel and has first passage and be communicated with corresponding first passage.First passage is recessed in the supporting plane of back side panel on the opposite side of running shaft.Each second channel and being communicated with for a back pressure chamber of the pressing chamber in compression stage subsequently in back pressure chamber.When the opening of the circumferential surface of running shaft is during according to a relative positioning in the first passage of the rotation of running shaft and downstream passage, upstream passageway is communicated with the corresponding second channel of downstream passage by communication chamber.On the other hand, when the opening of the circumferential surface of running shaft is not during according to a first passage relative positioning in the first passage of the rotation of running shaft and downstream passage, between the corresponding second channel of upstream passageway and downstream passage, close by the connection of communication chamber.
The favourable part between running shaft and back side panel without the above-mentioned rotary vane compressor of sliding bearing is, has reduced the quantity of parts and has realized thus reduction manufacture cost.
In rotary vane compressor, wherein, depend on the position, angle of running shaft, rotating channel can with being communicated with for a back pressure chamber of the pressing chamber in compression stage subsequently in discharge chamber and back pressure chamber, extreme pressure lubricant is supplied to off and on for each back pressure chamber of the pressing chamber in compression stage subsequently, and therefore, press off and on the internal surface of rotor chamber for the blade of back pressure chamber.Therefore, blade is lubricated and prevents the vibration of blade in corresponding blade groove.In addition, prevent that refrigerant gas from spilling from pressing chamber, therefore, improve the compression efficiency of compressor.
When discharge chamber is not communicated with any in back pressure chamber, when running shaft stops simultaneously, refrigerant gas is reverse flow and not counterrotating of running shaft not.Even if running shaft stops, discharge chamber is positioned to any back pressure chamber in back pressure chamber and is communicated with simultaneously, if refrigerant gas is reverse flow and running shaft counterrotating slightly slightly, the position, angle of running shaft changes so, therefore, discharge chamber is closed and being communicated with of back pressure chamber, and makes no longer reverse flow and no longer counterrotating of running shaft of refrigerant gas.Therefore, rotary vane compressor prevents the reverse flow of refrigerant gas and the counterrotating of running shaft reliably and promptly.
The rotary vane compressor that is formed with rotating channel in running shaft does not need the space for the valve such as safety check, thereby the size of limit compression machine increases.Rotating channel in running shaft is easy to processing, and this reduces the problem relevant to the compressor of exploitation Multiple Type.
But, at the first passage of the part of the downstream passage as back pressure applying mechanism along the circumferencial direction of cylindrical supporting plane partly in the rotary vane compressor in recessed back side panel, this first passage is difficult to process and therefore, be difficult to further reduce the processing cost of compressor.
In rotary vane compressor, the first passage being formed on the opposite side of running shaft in cylindrical supporting plane may broaden along the circumferencial direction of running shaft for being convenient to process the object of first passage, rotating channel is difficult to close and being communicated with of first passage thus, and this can make refrigerant gas reverse flow and running shaft counterrotating.
Considered a kind of rotary vane compressor of the present invention is directed to of above problem, it has been realized reduction manufacture cost and has prevented reliably refrigerant gas reverse flow and running shaft counterrotating.
Summary of the invention
According to an aspect of the present invention, rotary vane compressor comprises housing, a pair of front side plate and back side panel, rotation axis body, rotor, multiple blade and back pressure applying mechanism.Housing has suction chamber and discharge chamber.Thereby this is fixedly placed in housing and forms rotor chamber between front side plate and back side panel front side plate and back side panel.Back side panel has cylindrical supporting plane.Rotation axis body is rotatably supported in housing and extends through rotor chamber.Rotation axis body has the circumferential surface relative with the supporting plane of back side panel.Rotor arrangements in rotor chamber and can with rotation axis body synchronous rotary.Rotor has multiple blade grooves.Thereby blade is received in slidably and in blade groove, forms multiple back pressure chambers.Blade is combined the multiple pressing chambers of formation with the inner peripheral surface of rotor chamber, outer circumferential face, front side plate and the back side panel of rotor.Back pressure applying mechanism be arranged to by the pressure in discharge chamber be applied in back pressure chamber at least one back pressure chamber of the pressing chamber in compression stage subsequently.Rotary vane compressor is characterised in that, back pressure applying mechanism has upstream passageway, communication chamber, rotating channel and downstream passage.Thereby upstream passageway is formed in back side panel from discharge chamber and extends to supporting plane and upstream passageway has opening at supporting plane.The rear end of the contiguous rotation of communication chamber axis body forms.Rotating channel extends through rotation axis body and arrives the circumferential surface of rotation axis body and have opening at circumferential surface from communication chamber.Thereby downstream passage is formed in back side panel and allows communication chamber and being communicated with at least one back pressure chamber of the pressing chamber in compression stage subsequently in back pressure chamber.Upstream passageway is communicated with communication chamber by the opening of back side panel and the opening of rotation axis body off and on according to the rotation of rotation axis body.
In following description by reference to the accompanying drawings, other aspects of the present invention and advantage will become apparent, and accompanying drawing illustrates principle of the present invention by example.
Brief description of the drawings
With reference to the following description of current preferred implementation and accompanying drawing, the present invention may be better understood and object of the present invention and advantage, in the accompanying drawings:
Fig. 1 is the longitdinal cross-section diagram that the rotary vane compressor of first embodiment of the invention is shown;
Fig. 2 is the sectional view intercepting along the line II-II in Fig. 1;
Fig. 3 is the partial section that the rear portion of the rotary vane compressor of Fig. 1 is shown;
Fig. 4 illustrates cross sectional view after the rear case of rotary vane compressor of Fig. 1 and the part of back side panel, in Fig. 4, for clear, has removed the separator of rotary vane compressor;
Fig. 5 A is cross sectional view after the part of the rotary vane compressor of Fig. 1 is amplified, and Fig. 5 A illustrates upstream passageway in the back side panel that is formed on Fig. 4 and is formed on the state that the rotating channel in the running shaft of compressor communicates with each other;
Fig. 5 B is cross sectional view after the part of the rotary vane compressor of Fig. 1 is amplified, and Fig. 5 B illustrates upstream passageway in the back side panel of Fig. 4 and the rotating channel disconnected state each other in running shaft;
Fig. 6 is similar to Fig. 3, but Fig. 6 illustrates the rear portion of rotary vane compressor second embodiment of the invention;
Fig. 7 A is cross sectional view after the part of the rotary vane compressor of Fig. 6 is amplified, and Fig. 7 A illustrates upstream passageway in the back side panel that is formed on compressor and is formed on the state that the rotating channel in the running shaft of compressor communicates with each other;
Fig. 7 B is cross sectional view after the part of the rotary vane compressor of Fig. 6 is amplified, and Fig. 7 B illustrates the rotating channel disconnected state each other in the running shaft of upstream passageway in the back side panel of compressor and compressor;
Fig. 8 A amplifies rear cross sectional elevation according to the part of the rotary vane compressor of the 3rd mode of execution of the present invention, and Fig. 8 A illustrates the upstream passageway in the back side panel that is formed on compressor and is formed on the state that the rotating channel in the running shaft of compressor communicates with each other;
Fig. 8 B is cross sectional view after amplifying according to the part of the rotary vane compressor of the 3rd mode of execution of the present invention, and Fig. 8 B illustrates the rotating channel disconnected state each other in the running shaft of upstream passageway in the back side panel of compressor and compressor;
Fig. 9 is similar to Fig. 3, but Fig. 9 illustrates according to the rear portion of the rotary vane compressor of the 4th mode of execution of the present invention;
Figure 10 A is cross sectional view after the part of the rotary vane compressor of Fig. 9 is amplified, and Figure 10 A illustrates upstream passageway in the back side panel that is formed on compressor and is formed on the state that the rotating channel in the running shaft of compressor communicates with each other; And
Figure 10 B is cross sectional view after the part of the rotary vane compressor of Fig. 9 is amplified, and Figure 10 B illustrates the rotating channel disconnected state each other in the running shaft of upstream passageway in the back side panel of compressor and compressor.
Embodiment
The rotary vane compressor of first embodiment of the invention to the four mode of executions is below described with reference to the accompanying drawings.
See figures.1.and.2, the rotary vane compressor of the first mode of execution comprises front case 1, is engaged to the rear case 2 of front case 1 and is fixedly mounted in the cylinder body 3 in rear case 2.Front case 1, rear case 2 and cylinder body 3 are combined formation housing of the present invention.
Front side plate 4 and back side panel 5 are fixedly mounted in respectively in front case 1 and rear case 2, thereby close two of cylinder body 3 ends to axial, form thus the rotor chamber 3A in the cross section with ovalize, as being clearly shown that in Fig. 2 in cylinder body 3.
Front side plate 4 and back side panel 5 have the axial bore 4A, the 5A that run through front side plate 4 and back side panel 5, and the inner peripheral surface of axial bore 4A, 5A forms respectively cylindrical supporting plane 4B, 5B.On the rear surface of front side plate 4 He in axial bore 4A, be formed with sliding layer 4C.Sliding layer 4C is formed on the upper sliding layer 4C simultaneously of supporting plane 4B and is formed on the rear surface of front side plate 4.On the front surface of back side panel 5 He in axial bore 5A, be formed with sliding layer 5C.Sliding layer 5C is formed on the upper sliding layer 5C simultaneously of supporting plane 5B and is formed on the front surface of back side panel 5.Sliding layer 4C and 5C are by zinc-plated formation.Running shaft 9 extend through rotor chamber 3A and be rotatably supported on front case 1 and the axial bore 4A and 5A of rear case 2 in.Thereby shaft sealer 7 between front case 1 and front side plate 4 around and sealing rotary rotating shaft 9.Running shaft 9 is as rotation axis body of the present invention.
Running shaft 9 extends through the axial bore 1A of front case 1 and magnetic clutch or pulley (not shown) is installed regularly on the front end of running shaft 9 at its front end.Magnetic clutch or pulley are operatively connected to car engine or thereby vehicle motor receives driving force from car engine or vehicle motor.Running shaft 9C has the cylindrical circumference face 9C relative with the supporting plane 5B of back side panel 5 in its back-end.
The rotor 10 with circular cross-section is fixedly mounted on running shaft 9 and is arranged in rotor chamber 3A.Rotor 10 has five blade groove 10A in its outer circumferential face, and each blade groove radially extends, as shown in Figure 2.Thereby blade 11 is received in slidably and in each blade groove 10A, forms cylindrical back pressure chamber 40., each back pressure chamber 40 is formed between the bottom of blade 11 and the internal surface of blade groove 10A.The outer circumferential face of blade 11, rotor 10, the inner peripheral surface of cylinder body 3, the internal surface of front side plate 4 and the internal surface of back side panel 5 are combined five pressing chambers 12 of formation.
Between front case 1 and front side plate 4, be formed with suction chamber 13, as shown in fig. 1.Front case 1 has import 1B at its top, and suction chamber 13 is connected to external refrigerant loop (not shown) by import 1B.Front side plate 4 has two inlet hole 4D(that run through front side plate 4 hole is only shown), suction chamber 13 is communicated with the suction space 3B forming through cylinder body 3 respectively by two inlet hole 4D.Each suction chamber 3B is communicated with the pressing chamber 12 in its sucting stage subsequently by being formed on two suction port 3C in cylinder body 3, as shown in Figure 2.
Between cylinder body 3 and rear case 2, be formed with two and discharge space 3D.The pressing chamber 12 of discharging the stage at it is communicated with a discharge space of discharging in the 3D of space via three exhaust port 3E that are formed in cylinder body 3.Discharge space 3D for each three expulsion valves 14 and three retainers 15 are provided.Each expulsion valve 14 is for opening and cut out its exhaust port 3E and each retainer 15 for limiting opening of its expulsion valve 14.
With reference to Fig. 3 and Fig. 4, back side panel 5 comprises the protuberance 5N with predetermined thickness at its rear side.Protuberance 5N has shaft sleeve part 5E, top 5F and bottom 5G.Thereby shaft sleeve part 5E extends back around running shaft 9.The thickness of the Thickness Ratio shaft sleeve part 5E that top 5F has is little and be formed in the upper part of back side panel 5, thereby in opposite direction from shaft sleeve part 5E side extending.Bottom 5G is formed in the lower part of back side panel 5 and from top 5F to downward-extension.Bottom 5G has the thickness substantially the same with top 5F.As shown in Figure 4, top 5F has therein two and discharges groove 5H and 5I, two discharge groove 5H and 5I from contiguous position, the top of top 5F dividually to downward-extension.Top 5F has the tap hole 5J and the 5K that run through top 5F at the lower end of discharging groove 5H and 5I, and tap hole 5J and 5K are communicated with discharge space 3D separately.
Between back side panel 5 and rear case 2, be formed with discharge chamber 16, as shown in fig. 1.In discharge chamber 16, be furnished with centrifugal separator 50, and centrifugal separator 50 remains between back side panel 5 and rear case 2 regularly.As shown in Figure 3, separator 50 comprises end frame 17 and cylindrical member 18, and cylindrical member 18 vertically extends and is fixedly mounted in end frame 17.
End frame 17 has the cylindrical oil separation chamber 17A of vertical extension therein.Cylindrical member 18 is force-fitted in oil separation chamber 17A in the upper end of oil separation chamber 17A.A part of oil separation chamber 17A provides guide surface 17B, and guide surface 17B guides the refrigerant gas of discharging from pressing chamber 12 around the outer circumferential face of cylindrical member 18.As shown in Figure 3, end frame 17 has pair of separated hole 17C(a sorting hole 17C is only shown).Sorting hole 17C is communicated with discharge groove 5H and 5I separately, and is also communicated with the space being formed between outer circumferential face and the guide surface 17B of cylindrical member 18.
End frame 17 has intercommunicating pore 17E in its lower end, and oil separation chamber 17A is communicated with discharge chamber 16 by intercommunicating pore 17E.Communication chamber 17F is formed by the shaft sleeve part 5E of end frame 17, back side panel 5 and the rear end of running shaft 9, as shown in Figure 3.
Back side panel 5 has a pair of oily recess 5Q in surface (or front surface) therein, and the cross section of each oily recess 5Q is fan-shaped, as shown in Fig. 2, Fig. 4, Fig. 5 A and 5B.According to the rotation of rotor 10, each oily recess 5Q be communicated with for the back pressure chamber 40 of the pressing chamber 12 in sucting stage or compression stage subsequently.As shown in Figure 1 and Figure 3, back side panel 5 has the valve opening 5D that runs through back side panel 5, and oily recess 5Q is communicated with discharge chamber 16 by valve opening 5D.In valve opening 5D, be furnished with ball member 20 and spring 19.Spring 19 promotes valve member 20 towards discharge chamber 16.In the time that rotary vane compressor starts, valve member 20 prevents that blade 11 from trembleing.
The bottom 5G of back side panel 5 has upstream passageway 5M therein, and upstream passageway 5M extends upwardly to supporting plane 5B from the bottom of bottom 5G, as shown in Figure 3.Upstream passageway 5M has the opening 5X that is formed on supporting plane 5B place.
Running shaft 9 has the central axial bore 9A extending from the rear end of running shaft 9 along the axial direction of running shaft 9 and the radial hole 9B radially extending to circumferential surface 9C from the front end of axial bore 9A therein, and running shaft 9 has the opening 9X that is formed on circumferential surface 9C place, as shown in Fig. 3, Fig. 5 A and Fig. 5 B.Axial bore 9A and radial hole 9B combine formation rotating channel of the present invention and extend to communication chamber 17F from circumferential surface 9C.
Back side panel 5 has two downstream passage 5P that run through back side panel 5, and two downstream passage 5P extend to the front surface of back side panel 5 from the rear surface of shaft sleeve part 5E.Each downstream passage in downstream passage 5P is communicated with communication chamber 17F on the one hand, and on the other hand can with being communicated with at least one back pressure chamber of the pressing chamber 12 in compression stage subsequently in back pressure chamber 40.Downstream passage 5P is formed as not being recessed in supporting plane 5B.Back pressure applying mechanism of the present invention comprise in order to the pressure in discharge chamber 16 is applied in back pressure chamber 40 for upstream passageway 5M, radial hole 9B, axial bore 9A, communication chamber 17F and the downstream passage 5P of at least one back pressure chamber of the pressing chamber 12 in compression stage subsequently.
As shown in fig. 1, rear case 2 has outlet 2A at its top, and discharge chamber 16 is connected to external refrigerant loop (not shown) by outlet 2A.Outlet 2A is positioned at above cylindrical member 18.Although it is all not shown in arbitrary accompanying drawing,, outlet 2A is connected to external refrigerant loop, and in outside refrigerant circuit, condenser, expansion valve and vaporizer are connected by pipeline with this order.Vaporizer is connected to the import 1B of compressor by pipeline.The air-conditioning that is formed for using in vehicle is combined in rotary vane compressor and external refrigerant loop.
In the time that driving force is transmitted from car engine (not shown), running shaft 9 rotates.In the operating process of above-mentioned rotary vane compressor, rotor 10 and running shaft 9 synchronous rotaries, change the volume of pressing chamber 12 thus.Therefore, flow in suction chamber 13 by import 1B through the refrigerant gas of the vaporizer in external refrigerant loop.Refrigerant gas in suction chamber 13 is drawn in pressing chamber 12 by inlet hole 4D, suction space 3B and suction port 3C.In pressing chamber 12, the refrigerant gas of compression flows to tap hole 5J or the 5K shown in Fig. 4 by exhaust port 3E and discharge space 3D.Refrigerant gas in tap hole 5J or 5K flows towards the guide surface 17B of the centrifugal separator 50 shown in Fig. 3 by discharging groove 5H or 5I and sorting hole 17C.Subsequently, refrigerant gas flows around cylindrical member 18 along guide surface 17B, and the lubricant oil that makes to be included in refrigerant gas separates by centrifugal action and refrigerant gas.The lubricant oil separating is flow in oil separation chamber 17A and is stored in the bottom of discharge chamber 16 by intercommunicating pore 17E.
When as shown in Figure 5 A, the opening 5X of upstream passageway 5M is at the predetermined angle position place of running shaft 9 or near this predetermined angle position during with relative the positioning of opening 9X of rotating channel, and upstream passageway 5M is communicated with communication chamber 17F by rotating channel discharge chamber 16 can be communicated with each back pressure chamber 40.Therefore, allow the extreme pressure lubricant in discharge chamber 16 to be supplied in each back pressure chamber 40 by upstream passageway 5M, radial hole 9B, axial bore 9A, communication chamber 17F and downstream passage 5P.In the rotary vane compressor of present embodiment, wherein, in the time that upstream passageway 5M is communicated with radial hole 9B, two downstream passage 5P are communicated with single communication chamber 17F and back pressure chamber 40, make the extreme pressure lubricant in discharge chamber 16 be tending towards being supplied to equably each back pressure chamber 40.
On the other hand, when as shown in Figure 5 B, the opening 5X of upstream passageway 5M is not near the position, angle of running shaft 9 or this position, angle during with relative the positioning of opening 9X of rotating channel, being communicated with between upstream passageway 5M and communication chamber 17F by axial bore 9A and radial hole 9B closes, and being communicated with also between discharge chamber 16 and back pressure chamber 40 closed.Therefore, the extreme pressure lubricant in discharge chamber 16 is fed in upstream passageway 5M, and is not fed in each back pressure chamber 40 by radial hole 9B and axial bore 9A.
, extreme pressure lubricant is supplied to off and on for each back pressure chamber 40 of the pressing chamber 12 in compression stage subsequently, and therefore, presses the internal surface of rotor chamber 3A for the blade 11 of back pressure chamber 40.Therefore, the blade 11 in blade groove 10A has been lubricated and has been prevented the vibration of blade 11.In addition, prevented that refrigerant gas from spilling from pressing chamber 12, and therefore, improved the compression efficiency of pressing chamber.
Lubricant oil is supplied to off and on and reliably in back pressure chamber 40 and allows the pressure in back pressure chamber 40 to adjust.Therefore, make the power that blade 11 presses the internal surface of rotor chamber 3A reduce and therefore, reduce for the power of operate compressor.
In the time closing that simultaneously running shaft 9 stops being communicated with between radial hole 9B and upstream passageway 5M, the counterrotating of the reverse flow of refrigerant gas and running shaft 9 can not occur.Even if running shaft 9 stops simultaneously radial hole 9B and is positioned at upstream passageway 5M and is communicated with, as shown in Figure 5 A, the position, angle subsequently of running shaft 9 also can be because the counterrotating slightly of the reverse flow slightly of refrigerant gas and running shaft 9 changes, and therefore, radial hole 9B closes and being communicated with of upstream passageway 5M, as shown in Figure 5 B, make no longer reverse flow and no longer counterrotating of running shaft 9 of refrigerant gas.Therefore, the rotary vane compressor of present embodiment prevents the reverse flow of refrigerant gas and the counterrotating of running shaft 9 reliably.
The back pressure applying mechanism that comprises upstream passageway 5M, radial hole 9B, axial bore 9A, communication chamber 17F and downstream passage 5P does not need recess, for example the partly first passage of recessed downstream passage of the circumferencial direction along cylindrical supporting plane in background technique., the back pressure applying mechanism of the rotary vane compressor of present embodiment saves the processing of the part recess of this formation of the circumferencial direction along supporting plane 5B.Therefore, the rotary vane compressor of present embodiment is conducive to the processing of its parts and realizes thus the further reduction of its processing cost.
The rotary vane compressor of present embodiment does not need recess, for example in background technique may be for passageway machining object and the first passage of the downstream passage that broadens along the circumferencial direction of running shaft easily.Therefore, radial hole 9B is easy to be communicated with upstream passageway 5M or closes and being communicated with of upstream passageway 5M.Therefore, rotary vane compressor is difficult to make refrigerant gas reverse flow and running shaft counterrotating.
As shown in Fig. 3, Fig. 5 A and Fig. 5 B, radial hole 9B can be communicated with upstream passageway 5M near the predetermined angle position place of running shaft 9 or this predetermined angle position.In the time that radial hole 9B is communicated with upstream passageway 5M, thereby the lubricant oil in communication chamber 17F is fed into lubricating bearing face 5B and circumferential surface 9C in the gap between supporting plane 5B and circumferential surface 9C.On the other hand, in the time that being communicated with between radial hole 9B and upstream passageway 5M closes, extreme pressure lubricant in discharge chamber 16 can not be supplied in radial hole 9B and axial bore 9A, but is supplied in the gap between supporting plane 5B and circumferential surface 9C by the rotation of running shaft 9.Therefore, between running shaft 9 and back side panel 5, do not have in the rotary vane compressor of sliding bearing, running shaft 9 can be rotated reposefully.
Therefore, the rotary vane compressor of present embodiment is realized the further reduction of its processing cost and is prevented reliably the reverse flow of refrigerant gas and the counterrotating of running shaft 9.
The zinc-plated sliding layer 4C of use of present embodiment and the rotary vane compressor of 5C reduce in side plate 4,5 and the sliding friction between the rotor 10 between side plate 4 and side plate 5.Sliding layer 5C can be formed on the front surface that is simultaneously formed on back side panel 5 on supporting plane 5B.Forming this sliding layer 4C and 5C does not need special process, thereby reduces reliably the manufacture cost of compressor.
In addition, the central hole being formed in running shaft 9 does not need special axial bore as the rotary vane compressor of axial bore 9A, thereby further reduces the manufacture cost of compressor.
The rotary vane compressor of the second mode of execution has two axial notch 9D, and two axial notch 9D are recessed in the circumferential surface 9C of running shaft 9, as shown in Fig. 6, Fig. 7 A and Fig. 7 B.Axial notch 9D is with respect to the axis symmetry of running shaft 9.The space being formed by axial notch 9D is as rotating channel of the present invention.Each axial notch 9D has opening 9Y at circumferential surface 9C place.All the other structures of the second mode of execution are substantially identical with the corresponding construction of the first mode of execution.
In the rotary vane compressor of present embodiment, upstream passageway 5M is communicated with off and on and alternately with axial notch 9D with the rotation of running shaft 9.Therefore, the higher pressure refrigerant gas in discharge chamber 16 is supplied in each back pressure chamber 40 off and on.Although in the first embodiment, upstream passageway 5M and radial hole 9B are because each complete rotation of running shaft 9 communicates with each other, as shown in Figure 5A and 5B, but, in the second mode of execution, upstream passageway 5M is because each half rotation of running shaft 9 communicates with each other, as shown in Figure 7A and 7B.Therefore,, in the second mode of execution, communicating with each other of upstream passageway 5M and axial notch 9D is more frequent than communicating with each other of the upstream passageway 5M in the first mode of execution and radial hole 9B.Therefore,, than the first mode of execution, the second mode of execution is more easily supplied in each back pressure chamber 40 extreme pressure lubricant in discharge chamber 16.
In the time that an axial notch in axial notch 9D is communicated with upstream passageway 5M near the predetermined angle position place of running shaft 9 or this predetermined angle position, as shown in Figure 6, the extreme pressure lubricant in discharge chamber 16 is fed in axial notch 9D.In the second mode of execution, the opening area of the axial notch 9D relative with supporting plane 5B is greater than the opening area of relative with supporting plane 5B in the first embodiment radial hole 9B.Therefore, in the time that running shaft 9 rotates, than the first mode of execution, the second mode of execution is more easily supplied in the gap between supporting plane 5B and circumferential surface 9C extreme pressure lubricant, and this allows the proper lubrication of running shaft 9.
The rotary vane compressor that axial notch 9D is formed in circumferential surface 9C is conducive to its processing, and therefore, realizes the further attenuating of processing cost.Other effects of the second mode of execution are substantially the same with the effect of the first mode of execution.
The rotary vane compressor of the 3rd mode of execution have substitute the first mode of execution sliding layer 5C by such as PTFE(or teflon) the sliding layer 5S that makes of fluorine resin, as shown in Fig. 8 A and Fig. 8 B.Sliding layer 5S is formed on the circumferential surface 9C relative with supporting plane 5B back side panel 5 running shaft 9.Similarly, sliding layer is formed on the circumferential surface 9C relative with supporting plane 4B front side plate 4 running shaft 9.
Running shaft 9 has from the axially extended axial bore 9A in rear end of running shaft 9 and radially extends to two radial hole 9E of circumferential surface 9C from the front end of axial bore 9A.Radial hole 9E opens at circumferential surface 9C place in the mode of the axis symmetry with respect to running shaft 9.In the present embodiment, axial bore 9A and radial hole 9E combine formation rotating channel of the present invention and extend to communication chamber 17F from circumferential surface 9C.All the other structures of the 3rd mode of execution are substantially the same with the corresponding construction of the first mode of execution.
The rotary vane compressor of present embodiment uses the fluorine resin such as PTFE to sliding layer, the friction factor of this sliding layer is less than the friction factor of zinc-plated slip surface, is further reduced in thus side plate 4,5 and the sliding friction between the rotor 10 between side plate 4 and side plate 5.Other effects of the 3rd mode of execution are substantially the same with the effect of the second mode of execution.
The rotary vane compressor of the 4th mode of execution shown in Fig. 9, Figure 10 A and Figure 10 B does not have such as 4C, the 4C of the first mode of execution to the three mode of executions and the sliding layer of 5S.In the present embodiment, the bearing bed 4B of front side plate 4 and back side panel 5 contacts with circumferential surface 9C with 5B.All the other structures of the 4th mode of execution are substantially the same with the corresponding construction of the first mode of execution.
Not having such as the rotary vane compressor of the sliding layer of 4C, 4C and 5S of present embodiment contributes to reduce manufacture cost.Other effects of the 4th mode of execution are substantially the same with the effect of the second mode of execution with the first mode of execution.
Although described the present invention under the background of the first mode of execution to the four mode of executions,, those skilled in the art are appreciated that the present invention can implement without departing from the scope of the invention in many ways.
For example, the rotation axis body of rotary vane compressor can comprise multiple parts., rotation axis body is not limited to running shaft, but can have any part that can synchronously rotate with running shaft.
Claims (6)
1. a rotary vane compressor, comprising:
Housing (1,2,3), described housing (1,2,3) has suction chamber (13) and discharge chamber (16);
A pair of front side plate (4) and back side panel (5), described a pair of front side plate (4) and back side panel (5) be fixedly placed on described housing (1,2,3) thus between described front side plate (4) and described back side panel (5), form rotor chamber (3A), described back side panel (5) has cylindrical supporting plane (5B);
Rotation axis body (9), described rotation axis body (9) is rotatably supported in described housing (1,2,3) and extends through described rotor chamber (3A), and described rotation axis body (9) has the circumferential surface (9C) relative with the described supporting plane (5B) of described back side panel (5);
Rotor (10), described rotor (10) be arranged in described rotor chamber (3A) and can with described rotation axis body (9) synchronous rotary, described rotor (10) has multiple blade grooves (10A);
Multiple blades (11), described multiple blade (11) be received in slidably corresponding described blade groove (10A) thus in form multiple back pressure chambers (40), wherein, described blade (11) is combined the multiple pressing chambers of formation (12) with the inner peripheral surface of described rotor chamber (3A), the outer circumferential face of described rotor (10), described front side plate (4) and described back side panel (5); And
Back pressure applying mechanism (5M, 9A, 9B, 9D, 17F, 5P), described back pressure applying mechanism (5M, 9A, 9B, 9D, 17F, 5P) by the pressure in described discharge chamber (16) be applied in described back pressure chamber (40) at least one back pressure chamber of the described pressing chamber (12) in compression stage subsequently;
It is characterized in that,
Described back pressure applying mechanism (5M, 9A, 9B, 9D, 17F, 5P) comprise upstream passageway (5M), communication chamber (17F), rotating channel (9A, 9B, 9D) and downstream passage (5P), wherein, described upstream passageway (5M) be formed on described back side panel (5) thus in extend to described supporting plane (5B) from described discharge chamber (16), and described upstream passageway (5M) has the opening (5X) of locating at described supporting plane (5B), wherein, the rear end of the contiguous described rotation axis body of described communication chamber (17F) (9) forms, wherein, and described rotating channel (9A, 9B, 9D) extend to the described circumferential surface (9C) of described rotation axis body (9) by described rotation axis body (9) from described communication chamber (17F), and described rotating channel (9A, 9B, 9D) there is the opening (9X locating at described circumferential surface (9C), 9Y), wherein, described downstream passage (5P) be formed on described back side panel (5) thus in allow described communication chamber (17F) and being communicated with at least one back pressure chamber of the described pressing chamber (12) in described compression stage subsequently in described back pressure chamber (40), wherein, described upstream passageway (5M) according to the rotation of described rotation axis body (9) by the described opening (5X) of described back side panel (5) and the described opening (9X of described rotation axis body (9), 9Y) be communicated with off and on described communication chamber (17F).
2. rotary vane compressor according to claim 1, it is characterized in that, on at least one in described supporting plane (5B) and described circumferential surface (9C), be formed with sliding layer (4C, 5C, 5S), thereby reduce the sliding friction between described supporting plane (5B) and described circumferential surface (9C).
3. rotary vane compressor according to claim 2, is characterized in that, described sliding layer (5C, 5S) is formed in zinc-plated on described supporting plane (5B).
4. according to the rotary vane compressor described in any one in claims 1 to 3, it is characterized in that, described rotating channel (9A, 9B, 9D) has the axial bore (9A) extending along the axial direction of described rotation axis body (9) and the radial hole (9B) that radially extends to the described circumferential surface (9C) of described rotation axis body (9) from described axial bore (9A).
5. rotary vane compressor according to claim 4, is characterized in that, described axial bore (9A) is formed in the central hole in described rotation axis body (9).
6. according to the rotary vane compressor described in any one in claims 1 to 3, it is characterized in that, described rotating channel (9A, 9B, 9D) comprises the space being formed by axial notch (9D), and described axial notch (9D) is recessed in the described circumferential surface (9C) of described rotation axis body (9).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-061611 | 2013-03-25 | ||
| JP2013061611A JP6115228B2 (en) | 2013-03-25 | 2013-03-25 | Vane type compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104074760A true CN104074760A (en) | 2014-10-01 |
| CN104074760B CN104074760B (en) | 2015-12-02 |
Family
ID=51596282
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410111444.2A Expired - Fee Related CN104074760B (en) | 2013-03-25 | 2014-03-24 | Rotary vane compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6115228B2 (en) |
| CN (1) | CN104074760B (en) |
| BR (1) | BR102014006884A2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105736369A (en) * | 2014-12-25 | 2016-07-06 | 株式会社丰田自动织机 | Vane-type compressor |
| CN105909522A (en) * | 2015-02-25 | 2016-08-31 | 株式会社丰田自动织机 | Blade type compressor |
| CN109854506A (en) * | 2017-11-30 | 2019-06-07 | 株式会社丰田自动织机 | Vane compressor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016176445A (en) * | 2015-03-20 | 2016-10-06 | カルソニックカンセイ株式会社 | Gas compressor and method for manufacturing gas compressor |
| JP7211163B2 (en) | 2019-02-28 | 2023-01-24 | ブラザー工業株式会社 | printers and computer programs |
| KR102422215B1 (en) * | 2019-05-17 | 2022-07-18 | 김재호 | Air compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105736369A (en) * | 2014-12-25 | 2016-07-06 | 株式会社丰田自动织机 | Vane-type compressor |
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| CN109854506A (en) * | 2017-11-30 | 2019-06-07 | 株式会社丰田自动织机 | Vane compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6115228B2 (en) | 2017-04-19 |
| BR102014006884A2 (en) | 2015-10-20 |
| CN104074760B (en) | 2015-12-02 |
| JP2014185596A (en) | 2014-10-02 |
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