CN104074761A - Rotary blade compressor - Google Patents
Rotary blade compressor Download PDFInfo
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- CN104074761A CN104074761A CN201410120047.1A CN201410120047A CN104074761A CN 104074761 A CN104074761 A CN 104074761A CN 201410120047 A CN201410120047 A CN 201410120047A CN 104074761 A CN104074761 A CN 104074761A
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- live axle
- back pressure
- rotary vane
- vane compressor
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Abstract
The invention discloses a rotary blade compressor comprising a housing, a pair of front side plates and rear side plates, a driving shaft, a rotor, a plurality of blades, and a back pressure application mechanism.The back pressure application mechanism comprises a back pressure channel and a valve device. The rotary blade compressor is characterized in that the back pressure channel is provided with a rotary channel in a rotary shaft. The valve device comprises a valve body, which is disposed in the driving shaft to drive the shaft to rotate synchronously. The valve body structure can be used to reduce the effective cross section communicated with the flow of the rotary channel under the condition of the increased rotation speed of the rotary shaft.
Description
Technical field
The present invention relates to a kind of rotary vane compressor.
Background technique
Japanese unexamined utility model application communique N0.57-18796 discloses a kind of rotary vane compressor, and this rotary vane compressor comprises front case, cylinder body, back side panel, rear case, live axle, rotor, multiple blade and back pressure applying mechanism.
In cylinder body, have rotor chamber, rotor is arranged in this rotor chamber.Front case is positioned at the front of cylinder body for the front end of enclosed rotor chamber.Rear case is positioned at the rear of cylinder body and has suction chamber and discharge chamber.
Back side panel remains on the rear end for enclosed rotor chamber between cylinder body and rear case.Live axle is rotatably bearing in front case and rear case.Rotor be arranged on live axle in rotor chamber with live axle synchronous rotary.Rotor has multiple blade grooves, and corresponding blade is slidably received in blade groove.Between the bottom of blade and blade groove, be formed with respectively multiple back pressure chambers.
The internal surface of blade, rotor chamber, the outer surface of rotor, the rear surface of front case and the front surface of back side panel coordinate to form multiple pressing chambers.Each pressing chamber is communicated with suction chamber at its sucting stage, reduces its volume and is communicated with discharge chamber by expulsion valve in its discharge stage at its compression stage.
Back pressure applying mechanism comprises valve gap, valve plate, back pressure passage and control valve unit.Valve gap is fixed to the rear end of back side panel and has the upstream passageway being communicated with discharge chamber.Back side panel has and downstream passage for the back pressure chamber of the pressing chamber in its compression stage is communicated with at that time.Valve plate is rotatably arranged in valve gap and has the diameter larger than live axle.The rear end that valve plate is connected to live axle with live axle synchronous rotary.The center-aisle that valve plate has valve chamber and is communicated with upstream passageway and downstream passage.
Upstream passageway, valve chamber, center-aisle and downstream passage coordinate to form back pressure passage, and each back pressure chamber all can be communicated with discharge chamber by this back pressure passage.Control valve unit is arranged in valve chamber and comprises valve body, this valve body be moved with change according to the rotational speed of live axle valve chamber fluid be communicated with net sectional area.
Above-mentioned rotary vane compressor is for the air-conditioning equipment of vehicle.In the time that the rotational speed of live axle increases, valve body is moved the net sectional area of the fluid connection that reduces valve chamber, thereby make the lubricant oil in discharge chamber be difficult to flow in each back pressure chamber by back pressure passage, this has prevented that internal surface that blade exceedingly presses the internal surface of rotor chamber and therefore prevented blade and rotor chamber is by excessive wear, and consequently rotary vane compressor has improved its serviceability.In addition, because rotary vane compressor has reduced its power loss, therefore it has improved the fuel efficiency of vehicle.
But, comprising that at back pressure applying mechanism a part for valve plate and back pressure passage and control valve unit are arranged in the rotary vane compressor in valve plate, the number of the parts of compressor increases, thereby has increased manufacture cost and the size of compressor.
The present invention who considers above problem and propose aims to provide a kind of reduction manufacture cost and subtracts undersized rotary vane compressor.
Summary of the invention
According to aspects of the present invention, rotary vane compressor comprises housing, a pair of front side plate and back side panel, live axle, rotor, multiple blade and back pressure applying mechanism.Housing has suction chamber and discharge chamber.Front side plate and back side panel are arranged in housing regularly to form rotor chamber between front side plate and back side panel.Live axle is rotatably bearing in housing and extends through rotor chamber.Rotor be arranged in rotor chamber and can with live axle synchronous rotary.Rotor has multiple blade grooves.Blade is slidably received in corresponding blade groove to form multiple back pressure chambers.Blade coordinates to form multiple pressing chambers with the interior perimeter surface of rotor chamber, outer surface, front side plate and the back side panel of rotor.Back pressure applying mechanism be arranged for 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 at that time.Back pressure applying mechanism comprises back pressure passage and control valve unit.Back pressure passage allows discharge chamber to be communicated with each back pressure chamber.Control valve unit is arranged in back pressure passage.This rotary vane compressor is characterised in that, back pressure passage has the rotating channel being formed in live axle.Control valve unit comprise be arranged in live axle with the valve body of live axle synchronous rotary.Valve body is configured to the net sectional area of the fluid connection that reduces rotating channel in the case of the rotational speed of live axle increases.
Other aspects of the present invention and advantage will become obviously from the following description done by reference to the accompanying drawings, and accompanying drawing shows principle of the present invention by way of example.
Brief description of the drawings
With reference to the following description to current preferred implementation, can understand best the present invention and object and advantage in conjunction with the drawings, in the accompanying drawings:
Fig. 1 is the longitdinal cross-section diagram that shows the rotary vane compressor of first embodiment of the invention;
Fig. 2 is the sectional view intercepting along the line II-II in Fig. 1;
Fig. 3 is the partial section that shows the rear portion of the rotary vane compressor of Fig. 1;
Fig. 4 A is the rear elevational sectional view of for the sake of clarity having removed the part amplification of the rotary vane compressor of Fig. 1 of centrifugal separator, and it shows the means of communication at intermittence that upstream passageway is communicated with radial hole;
Fig. 4 B is and view like Fig. 4 category-A, but it shows and is communicated with means of communication at cut intermittence between upstream passageway and radial hole;
Fig. 5 is the part amplification sectional view that shows the control valve unit of the rotary vane compressor of Fig. 1, and wherein, the rotational speed of the live axle of compressor is relatively low;
Fig. 6 is and the similar view of Fig. 5, but shows control valve unit, and wherein the rotational speed of the live axle of compressor is relatively high;
Fig. 7 A has for the sake of clarity removed the rear elevational sectional view that the part of the rotary vane compressor of Fig. 1 of centrifugal separator is amplified, it shows that upstream passageway and radial hole communicate with each other in the time that the rotational speed of the live axle of compressor is relatively low intermittence means of communication and control valve unit;
Fig. 7 B is and view like Fig. 7 category-A, but its show connection between upstream passageway and radial hole in the time that the rotational speed of the live axle of compressor is relatively low pent intermittence means of communication and control valve unit;
Fig. 8 A has for the sake of clarity removed the rear elevational sectional view that the part of the rotary vane compressor of Fig. 1 of centrifugal separator is amplified, it shows that upstream passageway and radial hole communicate with each other in the time that the rotational speed of the live axle of compressor is relatively high intermittence means of communication and control valve unit;
Fig. 8 B is and view like Fig. 8 category-A, but its show connection between upstream passageway and radial hole in the time that the rotational speed of the live axle of compressor is relatively high cut intermittence means of communication and control valve unit;
Fig. 9 is the partial section at the rear portion of rotary vane compressor second embodiment of the invention;
Figure 10 is the rear elevational sectional view of for the sake of clarity having removed the part amplification of the rotary vane compressor of Fig. 9 of centrifugal separator, and it shows intermittently means of communication;
Figure 11 is the part amplification sectional view showing according to the control valve unit of the rotary vane compressor of the 3rd mode of execution of the present invention, and wherein, the rotational speed of the live axle of compressor is relatively low;
Figure 12 is and the similar view of Figure 11, but shows according to the control valve unit of the rotary vane compressor of the 3rd mode of execution of the present invention, and wherein, the rotational speed of the live axle of compressor is relatively high;
Figure 13 is the part amplification sectional view showing according to the control valve unit of the rotary vane compressor of the 4th mode of execution of the present invention, and wherein, the rotational speed of the live axle of compressor is relatively low;
Figure 14 is and the similar view of Figure 13, but it shows according to the control valve unit of the rotary vane compressor of the 4th mode of execution of the present invention, and wherein, the rotational speed of the live axle of compressor is relatively high;
Figure 15 is the part amplification sectional view showing according to the control valve unit of the rotary vane compressor of the 5th mode of execution of the present invention; And
Figure 16 is the part amplification sectional view showing according to the control valve unit of the rotary vane compressor of the 6th mode of execution of the present invention.
Embodiment
Below with reference to accompanying drawings the rotary vane compressor of first embodiment of the invention to the six mode of executions is described.The rotary vane compressor of each mode of execution is installed on vehicle a part for the refrigerant circuit to form the air-conditioning equipment using in vehicle.
Referring to figs. 1 through Fig. 3, the rotary vane compressor of the first mode of execution comprises housing 1, front side plate 3, back side panel 5, live axle 7, rotor 9, five blades 11 and back pressure applying mechanism 13A.
As shown in Figure 1, housing 1 comprises front case 15, rear case 17 and cylinder body 19.
Front case 15 is arranged in the front portion of rotary vane compressor and is formed with boss 15C.In front case 15, there is the first shell space 15A and import 15B.The first shell space 15A is communicated with external refrigerant loop (not shown) by import 15B.Boss 15C is arranged in the front portion of front case 15 and has the axial bore 15D being communicated with the first shell space 15A running through wherein.Shaft sealer 21 is arranged in the first shell space 15A.
Rear case 17 is arranged in the rear portion of rotary vane compressor and is engaged to front case 15 by multiple bolts (not shown).Rear case 17 has the second shell space 17A and outlet 17B.The second shell space 17A is communicated with external refrigerant loop (not shown) by outlet 17B.
Cylinder body 19 is fixedly mounted in rear case 17 in the position adjacent with front case 15.
Front side plate 3 and back side panel 5 are fixedly mounted in respectively in front case 15 and rear case 17, with the opposite shaft orientation end of closed cylinder 19, thereby in cylinder body 19, form the rotor chamber 19A with elliptic cross-section, as shown in Figure 2., the front end of 3A enclosed rotor chamber, rear surface 19A of front side plate 3 and the rear end of the front surface 5A enclosed rotor chamber 19A of back side panel.Cylinder body 19 has two and sucks space 19B, each suction space 19B all by be formed on multiple suction port 19C in cylinder body 19 with by after the pressing chamber 43 of description be communicated with.
Cylinder body 19 has two recess 19D in its outer surface, and described two recess 19D form two discharge space 19E between cylinder body 19 and rear case 17.Each discharge space 19E is all communicated with pressing chamber 43 by the multiple exhaust port 19F that are formed in cylinder body 19.
As shown in Figure 1, in each discharge space 19E, be provided with multiple expulsion valves 22 and multiple holder 23.Each expulsion valve 22 is used for opening and cut out exhaust port 19F associated with it and each holder 23 is used for limiting opening of expulsion valve associated with it 22.
As shown in Figure 1, between front case 15 and front side plate 3, be formed with suction chamber 25, and suction chamber 25 is communicated with external refrigerant loop (not shown) by import 15B.
Front side plate 3 has two the inlet hole 3C (only showing) that run through wherein.Front side plate 3 has the axial bore running through wherein, and the interior perimeter surface of axial bore forms cylindrical bearing surface 3B.By zinc-plated formation sliding layer 27A on the rear surface 3A at bearing surface 3B and front side plate 3.
Inlet hole 3C is connected to each other suction chamber 25 with the corresponding space 19B that sucks.
As shown in Figure 1, between back side panel 5 and rear case 17, be formed with discharge chamber 29, and discharge chamber 29 is communicated with external refrigerant loop (not shown) by outlet 17B.
As shown in Figure 3, back side panel 5 has boss 5B, cylindrical bearing surface 5C, upstream passageway 5D, two supply hole 5E, a pair of oily recess 5F and two first rows 31A (only showing) that portals.Boss 5B extends back from the central part of the rear surface 5G of back side panel 5.Bearing surface 5C extends axially towards the front surface 5A of back side panel 5 from the rear surface of boss 5B.By zinc-plated sliding layer 27B and the 27C of forming respectively on the front surface 5A at bearing surface 5C and back side panel 5.
Upstream passageway 5D vertically extends to bearing surface 5C from the bottom of back side panel 5.The upper end that discharge chamber 29 and upstream passageway 5D are led in the lower end of upstream passageway 5D is opened wide at bearing surface 5C place., upstream passageway 5D extends to bearing surface 5C from discharge chamber 29.
Each supply hole 5E all extends axially the front surface 5A to back side panel 5 from the rear surface of boss 5B.As shown in Figure 4 A and 4 B shown in FIG., each oily recess 5F all has sector crosssection.Oil recess 5F is formed in the front surface 5A of back side panel 5.It should be pointed out that for convenience of explanation, in Fig. 4 A and Fig. 4 B, saved by after describe clack box 47.
As shown in Figure 3, the first row 31A that portals extends to rear surface 5G from the front surface 5A of back side panel 5.First row portal 31A lead at its front end place discharge space 19E.
Centrifugal separator 33 is fixed to the rear end of the back side panel 5 being arranged in discharge chamber 29.Centrifugal separator 33 has end frame 35 and separator tube 37.
End frame 35 has recess 35A and is inserted in the rear surface 5G that is engaged to back side panel 5 in recess 35A by boss 5B.Therefore, between boss 5B and recess 35A or between back side panel 5 and end frame 35, be formed with communication chamber 39.Communication chamber 39 is communicated with supply hole 5E.
Cylindrical shape oil separation chamber 35C, the intercommunicating pore 35D that end frame 35 also has cylindrical guiding channel 35B, be communicated with guiding channel 35B and two second rows 31B (only showing) that portals.Guiding channel 35B is positioned at oil separation chamber 35C top.Guiding channel 35B allow the refrigerant gas of discharging from pressing chamber 43 along the internal surface of guiding channel 35B around flowing.Intercommunicating pore 35D is positioned at the lower end of end frame 35 and oil separation chamber 35C and discharge chamber 29 is connected to each other.The second row 31B that portals on the one hand portals with corresponding first row that 31A is communicated with and is communicated with guiding channel 35B on the other hand.Each first row 31A and second row associated with it 31B that portals that portals will be connected to each other with this first row discharge space 19E and guiding channel 35B that 31A is associated that portal.
Separator tube 37 is positioned to coaxial with guiding channel 35B and is pressed into and is engaged in guiding channel 35B.Separator tube 37 locates to have the opening 37A of discharge chamber of being connected to 29 in the top.Separator tube 37 allows refrigerant gas to flow into wherein around the refrigerant gas flowing and allow lubricant oil to separate with it around it.
As shown in Figure 1, live axle 7 is inserted in housing 1 and by shaft sealer 21 and bearing surface 3B, 5C and is supported as rotating around the axes O of live axle 7 by axial bore 15D.
As shown in Figure 3, the rear end of live axle 7 extends out from back side panel 5, enters in communication chamber 39.As shown in Figure 5, live axle 7 has central hole 7A, radial hole 7B and putting chamber 7C in its rear portion.Central hole 7A is as axial bore of the present invention.Central hole 7A and radial hole 7B coordinate to form rotating channel of the present invention.As shown in Figure 1, live axle 7 also has the first peripheral surface 7D relative with bearing surface 5C and the second peripheral surface 7E relative with bearing surface 3B.The first peripheral surface 7D is as peripheral surface of the present invention.
As shown in Figure 5, central hole 7A extends along axes O towards the front end of live axle 7 from the rear end surface of live axle 7.Radial hole 7B is communicated with central hole 7A.Radial hole 7B radially extends to the first peripheral surface 7D and opens wide at the first peripheral surface 7D from the front side of central hole 7A.Radial hole 7B has the diameter identical with central hole 7A.Putting chamber 7C coaxially forms by the recessed cylindrical recess of the rear end surface from live axle 7 and central hole 7A.Therefore, putting chamber 7C is communicated with central hole 7A and radial hole 7B.Putting chamber 7C has than central hole 7A and the large diameter of radial hole 7B.
Central hole 7A, radial hole 7B and putting chamber 7C allow being communicated with and therefore allowing being communicated with between discharge chamber 29 and each supply hole 5E between upstream passageway 5D and communication chamber 39.Radial hole 7B, central hole 7A, putting chamber 7C, communication chamber 39, upstream passageway 5D and supply hole 5E coordinate to form the means of communication 100 at intermittence of carrying out being intermittently communicated with.
As shown in Figure 1, the front end of live axle 7 extends the first shell space 15A by boss 15C.Magnetic clutch or belt wheel (all not illustrating in the drawings) can be fixedly mounted on the front end of live axle 7.Magnetic clutch or belt wheel are operatively connected to vehicle motor or vehicle motor to receive driving force from vehicle motor or vehicle motor.
Rotor 9 is arranged in rotor chamber 19A and live axle 7 is pressed into and is engaged in rotor 9, make rotor 9 can with live axle 7 synchronous rotary in rotor chamber 19A.
As shown in Figure 2, to have cross section be circular drum to rotor 9.Rotor 9 has each 5 blade groove 9A that all radially extend at its outer surface place.Blade groove 9A separates with the angle intervals equating around axes O.Blade 11 is slidably received in each blade groove 9A, thereby forms back pressure chamber 41., each back pressure chamber 41 is all formed between the bottom of blade 11 and the internal surface of blade groove 9A.Number and the size of blade groove 9A and blade 11 are appropriately determin.
As shown in Figure 2, the back pressure chamber 41 for the pressing chamber 43 in its compression stage in back pressure chamber 41 is communicated with the supply hole 5E being associated.Along with the rotation of rotor 9, back pressure chamber 41 is communicated with an oily recess in oily recess 5F, and back pressure chamber 41 is communicated with other back pressure chamber 41 by this oil recess.In this way, back pressure chamber 41 can be communicated with discharge chamber 29.Therefore, lubricant oil is allowed to be supplied in each back pressure chamber 41 with higher pressure refrigerant gas.Each blade 11 all can be slided in corresponding blade groove 9A and from corresponding blade groove 9A and be skidded off by the pressure variation in its back pressure chamber 41.
Five blades 11, the interior perimeter surface of rotor chamber 19A, outer surface, front side plate 3 and the back side panels 5 of rotor 9 coordinate to form five pressing chambers 43.Pressing chamber 43 is connected to suction port 19C in its sucting stage, and pressing chamber 43 is connected to exhaust port 19F in its discharge stage.
As shown in Figure 3, putting chamber 7C, clack box 47, above-mentioned intermittence means of communication 100 and by after the back pressure passage 200 described coordinate to form back pressure applying mechanism 13A.
As shown in Figure 5 and Figure 6, bobbin 49 and coil spring 51 are arranged in clack box 47.Clack box 47, bobbin 49 and coil spring 51 coordinate to form control valve unit of the present invention.Bobbin 49 is used as pushing member of the present invention as valve body of the present invention and coil spring 51.
Clack box 47 is formed from a resin and is engaged in regularly in putting chamber 7C.Clack box 47 has guide hole 47B and the otch 47C of axially extended communicating passage 47A, radially extension.Communicating passage 47A has the first communicating passage 471 and the second communicating passage 472.The first communicating passage 471 is communicated with central hole 7A.The first communicating passage 471 and the second communicating passage 472 communicate with each other by guide hole 47B.The second communicating passage 472 locates to lead to communication chamber 39 in its back-end., in the situation that clack box 47 is fixed in putting chamber 7C, the first communicating passage 471 and the second communicating passage 472 coordinate not only to form a part for axial bore of the present invention, also form a part for rotating channel of the present invention.
Guide hole 47B is communicated with communicating passage 47A.In the situation that clack box 47 is fixed in putting chamber 7C, guide hole 47B towards the internal surface of putting chamber 7C with at its opposite end place by the inner surfaces enclose of putting chamber 7C.Spring seat 47D is formed in guide hole 47B.It should be pointed out that clack box 47 can be made up of aluminum alloy.
Bobbin 49 and coil spring 51 are arranged in guide hole 47B.Bobbin 49 has head 49A, the 49B of bar portion, skirt section 49C and the 49D of seat portion.Head 49A and the 49B of bar portion form each other.The 49B of bar portion extends through in skirt section 49C and the fixing present 49D of portion, makes head 49A and skirt section 49C between them, have passage 49E.As viewed in Fig. 5 and Fig. 6, coil spring 51, between the 49D of seat portion of spring seat 47D and bobbin 49, for pushing bobbin 49 downwards, makes head 49A be positioned closer to the axes O of live axle 7.Bobbin 49 can be in guide hole 47B against the pushing force radial motion of coil spring 51.,, as shown in Fig. 5 and Fig. 6 difference, bobbin 49 can move as making head 49A move or move away from axes O towards axes O in clack box 47.
As shown in Figure 5, in the time that the head 49A of bobbin 49 is positioned to the most close axes O, skirt section 49C contacts with spring seat 47D.Bobbin 49 is now located so that the first communicating passage 471 and the second communicating passage 472 align with passage 49E.
Upstream passageway 5D, radial hole 7B, central hole 7A, putting chamber 7C, communicating passage 47A, passage 49E, communication chamber 39, supply hole 5E and oily recess 5F coordinate to form back pressure passage 200.
In the rotary vane compressor of present embodiment, outlet 17B shown in Fig. 1 is connected to external refrigerant loop (not shown), in outside refrigerant circuit, condenser, expansion valve and vaporizer are connected by pipe with this order, and vaporizer is connected to the import 15B of compressor by pipe.Therefore, rotary vane compressor, external refrigerant loop and pipe are joined together to form the refrigerant circuit of the air-conditioning equipment using in vehicle.It should be pointed out that the diagram of having omitted pipe, condenser, expansion valve and vaporizer in figure.
In the time that driving force is transmitted from vehicle motor (not shown), live axle 7 rotates.At the run duration of above-mentioned rotary vane compressor, rotor 9 and live axle 7 synchronous rotaries, thereby the volume of change pressing chamber 43.Therefore, flow in suction chamber 25 by import 15B through the refrigerant gas of the vaporizer in external refrigerant loop.Refrigerant gas in suction chamber 25 is drawn in pressing chamber 43 to compress by inlet hole 3C, suction space 19B and suction port 19C.In pressing chamber 43, the refrigerant gas of compression is flow into and is discharged in the 19E of space by exhaust port 19F.Discharging refrigerant gas in the 19E of space flow in the guiding channel 35B between outer surface and the end frame 35 of separator tube 37 by first row 31A and the second row 31B that portals that portals.The lubricant oil being included in refrigerant gas is isolated from refrigerant gas by centrifugal separator 33.The refrigerant gas of having isolated lubricant oil flow in discharge chamber 29 by the opening 37A of separator tube 37, and isolated lubricant oil flows through oil separation chamber 35C and intercommunicating pore 35D to be retained in the bottom of discharge chamber 29.Refrigerant gas in discharge chamber 29 flows to condenser by outlet 17B.
Lubricant oil contained in refrigerant gas in discharge chamber 29 is supplied in each back pressure chamber 41 by back pressure passage 200 with part of refrigerant gas.Particularly, at lubricating oil flow, to before in corresponding back pressure chamber 41, lubricant oil flow in communication chamber 39 by the first communicating passage 471, passage 49E and second communicating passage 472 of the clack box 47 upstream passageway 5D, radial hole 7B, central hole 7A, putting chamber 7C from discharge chamber 29.Lubricant oil in communication chamber 39 is supplied to for the back pressure chamber 41 of the pressing chamber 43 in sucting stage or compression stage at that time by supply hole 5E.Lubricant oil in communication chamber 39 is supplied to for the back pressure chamber 41 of the pressing chamber 43 in sucting stage or compression stage at that time by supply hole 5E and oily recess 5F.
Comprise the intermittently run duration of the rotary vane compressor of means of communication 100 at back pressure applying mechanism 13A, as shown in Figure 4 A, in the time that radial hole 7B is communicated with upstream passageway 5D, discharge chamber 29 is communicated with communication chamber 39 and is further communicated with each back pressure chamber 41, makes lubricant oil in upstream passageway 5D be allowed through radial hole 7B and flow in communication chamber 39 and further flow in each back pressure chamber 41.
On the other hand, as shown in Figure 4 B, in the time that being communicated with between radial hole 7B and upstream passageway 5D is cut off, being communicated with also between upstream passageway 5D and communication chamber 39 is cut off, and makes the lubricant oil in upstream passageway 5D be prevented from flowing in communication chamber 39.Therefore, lubricant oil is prevented from flowing in each back pressure chamber 41.In this way, be communicated with the intermittence that intermittently means of communication 100 is rotated passage.,, according to the angular orientation of live axle 7, intermittently means of communication 100 makes rotating channel be communicated with discharge chamber 29 and each back pressure chamber 41 and cuts off this connection.
Being fixed on the run duration of clack box in putting chamber 7C 47 with the rotary vane compressor of live axle 7 synchronous rotaries, centrifugal action is on clack box 47 and bobbin 49 radial motion in the guide hole 47B of clack box 47 under the impact of this centrifugal force, as shown in Figure 5 and Figure 6.
Particularly, as shown in Figure 5, in the time that the rotational speed of live axle 7 is relatively low, owing to acting on, centrifugal force on clack box 47 is relatively little, and therefore the head 49A of bobbin 49 is mainly positioned adjacent to axes O by the pushing force of coil spring 51.Because passage 49E is positioned adjacent to the position that passage 49E aligns with communicating passage 47A, therefore the net sectional area that the fluid between the first communicating passage 471, the second communicating passage 472 and passage 49E is communicated with becomes relatively large, and the lubricant oil in radial hole 7B is flow in communication chamber 39 glibly by communicating passage 47A and passage 49E.,, in the time that the rotational speed of live axle 7 is relatively low, the net sectional area of the connection between the first communicating passage 471, the second communicating passage 472 and passage 49E becomes relatively large, and the net sectional area of the therefore connection of rotating channel becomes relatively large.Therefore the quantitative change that, flow in putting chamber 39 and therefore flow into the lubricant oil in each back pressure chamber 41 obtains relatively large.
On the other hand, as shown in Figure 6, in the time that the rotational speed of live axle 7 increases, because the centrifugal force acting on clack box 47 increases, therefore the head 49A of bobbin 49 moves away from axes O against the pushing force of coil spring 51.The position outward radial aliging with communicating passage 47A from passage 49E due to passage 49E moves, therefore the net sectional area of the connection between the first communicating passage 471, the second communicating passage 472 and passage 49E reduces, and therefore the lubricant oil in radial hole 7B becomes and is difficult to flow through communicating passage 47A and passage 49E.,, in the time that the rotational speed of live axle 7 increases, the net sectional area of connection and the net sectional area of the therefore connection of rotating channel between the first communicating passage 471, the second communicating passage 472 and passage 49E become relatively little.Therefore,, in the time that the rotational speed of live axle 7 increases, flow in communication chamber 39 and the amount that therefore flow to the lubricant oil in each back pressure chamber 41 reduces.It should be pointed out that bobbin 49 will not move to outside clack box 47, reason be guide hole 47B at its end opposite place the inner surfaces enclose by putting chamber 7C.
Motion at bobbin 49 in clack box 47 is in conjunction with in the above-mentioned rotary vane compressor that intermittence, means of communication 100 operation was carried out, as shown in Figure 7 A, in the time that the rotational speed of live axle 7 is relatively low and radial hole 7B is positioned to be communicated with upstream passageway 5D, the quantitative change that flow to the lubricant oil in communication chamber 39 obtains relatively large.As shown in Figure 8 A, in the time that the rotational speed of live axle 7 is relatively high and radial hole 7B is positioned to be communicated with upstream passageway 5D, the quantitative change that flow to the lubricant oil in communication chamber 39 obtains relatively little.
On the other hand, as shown in Fig. 7 B and Fig. 8 B, when radial hole 7B and upstream passageway 5D cut off while being communicated with, no matter how the rotational speed of live axle 7 all stops lubricating oil flow in communication chamber 39.
In the rotary vane compressor of present embodiment, the pressure in each back pressure chamber 41 can suitably be adjusted according to the rotational speed of live axle 7 as above.During live axle 7 High Rotation Speeds, prevented that blade 11 excessive compression are in the interior perimeter surface of rotor chamber 19A, thereby prevented the interior perimeter surface excessive wear of blade 11 and rotor chamber 19A, and rotary vane compressor improves its serviceability.In addition, the rotary vane compressor that has reduced its power loss due to the wearing and tearing that reduce can improve the fuel efficiency of vehicle.
In the rotary vane compressor of present embodiment, central hole 7A, radial hole 7B and putting chamber 7C---it is a part for an intermittence part for means of communication 100 or the back pressure passage 200 of back pressure applying mechanism 13A---are all formed in live axle 7.In addition, clack box 47 is arranged in the putting chamber 7C being formed in live axle 7.Because clack box 47 is arranged in live axle 7, so communicating passage 47A and passage 49E are also arranged in live axle 7.Although the rotary vane compressor of this structure exists central hole 7A, radial hole 7B, putting chamber 7C and clack box 47, size aspect does not increase.
Be arranged in the rotary vane compressor of the present embodiment in clack box 47 at bobbin 49 and coil spring 51, the structure of control valve unit is simplified.In addition, clack box 47 is fixed on simply and in putting chamber 7C, allows clack box 47 and live axle 7 synchronous rotaries.Be formed in the rotary vane compressor of the present embodiment in clack box 47 at guide hole 47B, guide hole 47B does not need to form and therefore do not open wide at the first peripheral surface 7D place through live axle 7.Therefore, back side panel 5 is supporting driving shaft 7 suitably, and wherein, bearing surface 5C contacts with the first peripheral surface 7D.
Be formed on front side plate 3 and sliding layer 27B and 27C are formed in the rotary vane compressor of the present embodiment on back side panel 5 at sliding layer 27A, the sliding friction between bearing surface 3B and the second peripheral surface 7E and between bearing surface 5C and the first peripheral surface 7D reduces.In the rotary vane compressor of present embodiment, do not need the bearing such as sliding bearing or rolling bearing of the sliding friction between bearing surface 3B for reducing and the second peripheral surface 7E and between bearing surface 5C and the first peripheral surface 7D.Therefore, prevented that the size of rotary vane compressor of present embodiment and the number of parts from increasing.
In the rotary vane compressor of present embodiment, sliding layer 27A reduces the sliding friction between the rear surface 3A of front side plate 3 and the front surface of rotor 9, and sliding layer 27C reduces the sliding friction between the front surface 5A of back side panel 5 and the rear surface of rotor 9.
Sliding layer 27A to 27C by zinc-plated formation can easily be manufactured.
Extend to from discharge chamber 29 at upstream passageway 5D the rotary vane compressor of present embodiment of the bearing surface 5C of back side panel 5, allow the lubricant oil in discharge chamber 29 to flow to swimmingly bearing surface 5C by the passage of simplifying.
Form in the rotary vane compressor of present embodiment of a part for rotating channel or a part for means of communication 100 at intermittence (or back pressure passage 200) at central hole 7A, in the time of formation means of communication 100 at intermittence and back pressure passage 200, prevented that the number of parts and manufacturing time from increasing.Therefore, intermittently means of communication 100 and back pressure passage 200 easily and at low cost form.
In the rotary vane compressor of present embodiment, can easily be formed in live axle 7 with the putting chamber 7C of the coaxial manufacture of central hole 7A.
Therefore, the rotary vane compressor of present embodiment has reduced size and the manufacture cost of compressor.
Comprise the intermittently run duration of the rotary vane compressor of the present embodiment of means of communication 100 at back pressure applying mechanism 13A, the interior perimeter surface that extreme pressure lubricant is supplied in each back pressure chamber 41 off and on and therefore blade 11 presses rotor chamber 19A.Therefore, the flutter lubricated and blade 11 of the blade 11 in blade groove 9A is prevented from.In addition, prevent the leakage of refrigerant gas from pressing chamber 43, and therefore improved the compression efficiency of compressor.Pressure in discharge chamber 29 is not only applied to each back pressure chamber 41 but also is provided with in the rotary vane compressor of the present embodiment of means of communication 100 intermittently according to the rotational speed of live axle 7, the power that blade 11 presses the internal surface of rotor chamber 19A can be adjusted according to the operation conditions of compressor.
In the rotary vane compressor of present embodiment, if discharge chamber 29 is not communicated with the arbitrary back pressure chamber in back pressure chamber 41 in the situation that stopping at live axle 7, there is not the counterrotating of live axle 7 in the reverse flow that lubricant oil neither occurs yet.Even if live axle 7 stops and discharge chamber 29 is communicated with the arbitrary back pressure chamber in back pressure chamber 41, the angular orientation of live axle 7 or radial hole 7B still changes by the slight reverse flow of lubricant oil and the slight counterrotating of live axle 7, and therefore, the cut-out that is communicated with by discharge chamber 29 with back pressure chamber 41, result lubricant oil is reverse flow and no longer counterrotating of live axle 7 no longer.Therefore, the rotary vane compressor of present embodiment prevents the reverse flow of lubricant oil and the counterrotating of live axle 7 reliably and in time.
In the rotary vane compressor of present embodiment, in the situation that clack box 47 is fixed in putting chamber 7C, guide hole 47B passes through the inner surfaces enclose of putting chamber 7C at its end opposite place.Therefore, do not need additional member for limiting motion or the motion of bobbin 49 in guide hole 47B of the bobbin 49 being pushed by coil spring 51.
With reference to Fig. 9 and Figure 10, the rotary vane compressor of the second mode of execution comprises the back pressure applying mechanism 13A of rotary vane compressor and the back pressure applying mechanism 13B of back side panel 5 and the back side panel 55 that substitute the first mode of execution.
Identical with the situation of the back side panel 5 in the first mode of execution, back side panel 55 is fixed in the second shell space 17A of rear case 17.Back side panel 55 has boss 55A, cylindrical bearing surface 55B and two first rows 31A (only showing) that portals.Boss 55A extends back from the central part of the rear surface 55D of back side panel 55.Bearing surface 55B extends axially towards the front surface 55C of back side panel 55 from the rear end of boss 55A.Sliding layer 27B and 27C are by zinc-plated formation on the bearing surface 55B of back side panel 55 and front surface 55C respectively.In addition, the end frame 35 of centrifugal separator 33 is engaged to the rear surface 55D of back side panel 55, thereby forms communication chamber 39 between end frame 35 and the rear surface 55D of back side panel 55.
Back side panel 55 has the first upstream passageway 55E, the second upstream passageway 55F, a pair of supply recess 55G and 55H, a pair of supply hole 55I and 55J and a pair of oily recess 55K.
The first upstream passageway 55E vertically extends through back side panel 55.The first upstream passageway 55E leads to discharge chamber 29 at its lower end.The second upstream passageway 55F extends axially in back side panel 55.The second upstream passageway 55F is connected to the upper end of the first upstream passageway 55E at its front end place, the second upstream passageway 55F locates to lead to communication chamber 39 in its back-end simultaneously.
As shown in figure 10, supply with recess 55G and 55H is formed as from bearing surface 55B recessed in back side panel 55.Supplying with recess 55G and 55H is positioned on the radially opposition side of live axle 7.It should be pointed out that for the sake of clarity, in Figure 10, omitted the diagram of clack box 47.As shown in Figure 9, supply hole 55I and 55J extend axially towards rotor 9 from corresponding supply recess 55G and 55H.The oily recess 55K of the second mode of execution has the essentially identical structure of oily recess 5F with the first mode of execution.
In the rotary vane compressor of present embodiment, central hole 7A, the radial hole 7B in putting chamber 7C and clack box 47 allow communication chamber 39 and supply with being communicated with between recess 55G or 55H., the central hole 7A in putting chamber 7C, radial hole 7B and clack box 47 allow being communicated with between discharge chamber 29 and supply hole 55I or 55J.Therefore, the first upstream passageway 55E and the second upstream passageway 55F, radial hole 7B, central hole 7A, putting chamber 7C, clack box 47, communication chamber 39, supply recess 55G and 55H and supply hole 55I and 55J coordinate to form intermittently means of communication 101.
In the present embodiment, the first upstream passageway 55E and the second upstream passageway 55F, radial hole 7B, central hole 7A, communicating passage 47A, passage 49E, communication chamber 39, supply recess 55G and 55H, supply hole 55I and 55J and oily recess 55K coordinate to form back pressure passage 201.
Back pressure passage 201, putting chamber 7C, clack box 47 and intermittently means of communication 101 coordinate to form back pressure applying mechanism 13B.All the other structures of the second mode of execution and the counter structure of the first mode of execution are basic identical.In Fig. 9 and Figure 10, identical reference character is for common elements or the element of the first mode of execution and the second mode of execution, and the description to these parts or element by omission.
In the rotary vane compressor of present embodiment, the lubricant oil in discharge chamber 29 by intermittence means of communication 101 be supplied in the manner as described below in each back pressure chamber 41., the lubricant oil in discharge chamber 29 flow in communication chamber 39 by the first upstream passageway 55E and the second upstream passageway 55F.Lubricant oil in communication chamber 39 flow in radial hole 7B by communicating passage 47A, passage 49E and central hole 7A subsequently.At the run duration of rotary vane compressor, as shown in Figure 9, in the time that radial hole 7B is communicated with supply recess 55G, the lubricant oil in radial hole 7B is supplied in each back pressure chamber 41 by supply hole 55I and each oily recess 55K.In the time that radial hole 7B is communicated with supply recess 55H, the lubricant oil in radial hole 7B is supplied in each back pressure chamber 41 by supply hole 55J and each oily recess 55K.
On the other hand, as shown in figure 10, when radial hole 7B is not when supplying with any in recess 55G and 55H and be communicated with, lubricant oil is prevented from being supplied in back pressure chamber 41.
In the rotary vane compressor of motion at bobbin 49 in clack box 47 in conjunction with the second mode of execution that means of communication 101 operation is carried out at intermittence, back pressure applying mechanism 13B has the essentially identical effect of back pressure applying mechanism 13A with the first mode of execution.Other effects of the second mode of execution and other effects of the first mode of execution are basic identical.
With reference to Figure 11 and Figure 12, the rotary vane compressor of the 3rd mode of execution comprises the live axle 7 of rotary vane compressor and the live axle 57 of back pressure applying mechanism 13A and the back pressure applying mechanism 13C that substitute the first mode of execution.
The guide hole 57C that live axle 57 has axial bore 57A, radial hole 57B and is communicated with axial bore 57A and radial hole 57B.Axial bore 57A, radial hole 57B and guide hole 57C coordinate to form rotating channel of the present invention.Live axle 57 also has the first peripheral surface 57D and the second peripheral surface (not shown).The first peripheral surface 57D is as peripheral surface of the present invention.
Axial bore 57A is parallel to the axes O of live axle 57 and extends and lead to communication chamber 39 at the rear end surface place of live axle 57 in live axle 57.Radial hole 57B hole 57A perpendicular to axial direction in live axle 57 extends and opens wide at the first peripheral surface 57D place.Guide hole 57C with respect to the axes O oblique line of live axle 57 be formed in live axle 57 and between axial bore 57A and radial hole 57B and extend.In addition, guide hole 57C is formed as making its diameter to reduce gradually to radial hole 57B from axial bore 57A.Guide hole 57C locates be communicated with axial bore 57A and be communicated with radial hole 57B at its front end place in its back-end.
Ball valve body 59 and coil spring 61 are arranged in guide hole 57C.Ball valve body 59 can in guide hole 57C, move and guide hole 57C and axial bore 57A between the net sectional area that is communicated with of fluid can change the position in guide hole 57C according to ball valve body 59.Coil spring 61 is towards the rear end of guide hole 57C pushes ball valve body 59., coil spring 61 is along the direction pushes ball valve body 59 that increases the net sectional area being communicated with between guide hole 57C and axial bore 57A.Ball valve body 59 and coil spring 61 are used separately as valve body of the present invention and pushing member.Guide hole 57C, ball valve body 59 and coil spring 61 coordinate to form control valve unit of the present invention.
The position of back-up ring 62A between axial bore 57A and guide hole 57C is engaged in live axle 57 regularly.Back-up ring 62A limits the motion of ball valve body 59 towards axial bore 57A by contact ball valve body 59.
In the rotary vane compressor of present embodiment, axial bore 57A, radial hole 57B and guide hole 57C allow being communicated with between upstream passageway 5D and communication chamber 39., axial bore 57A, radial hole 57B and guide hole 57C allow being communicated with between discharge chamber 29 and each supply hole 5E.Axial bore 57A, radial hole 57B, guide hole 57C, communication chamber 39, upstream passageway 5D and supply hole 5E coordinate to form intermittently means of communication 102.
Upstream passageway 5D, axial bore 57A, radial hole 57B, guide hole 57C, communication chamber 39, supply hole 5E and oily recess 5F coordinate to form back pressure passage 202.
Back pressure passage 202, guide hole 57C, ball valve body 59, coil spring 61 and intermittently means of communication 102 coordinate to form back pressure applying mechanism 13C.All the other structures of the 3rd mode of execution and the counter structure of the first mode of execution are basic identical.
In the rotary vane compressor of present embodiment, the lubricant oil in upstream passageway 5D flow in communication chamber 39 by radial hole 57B, guide hole 57C and axial bore 57A successively.In the time that live axle 57 rotates, the centrifugal action being produced by the rotation of live axle 57, on ball valve body 59, moves ball valve body 59, as shown in Figure 11 and Figure 12 in guide hole 57C.
Particularly, as shown in figure 11, in the time that the rotational speed of live axle 57 is relatively low, relatively little owing to acting on centrifugal force on ball valve body 59, therefore ball valve body 59 is positioned to mainly pushing force by coil spring 61 near axes O, makes the net sectional area of the connection of net sectional area that the fluid between axial bore 57A and guide hole 57C is communicated with or rotating channel become relatively large.Therefore the quantitative change that, flow to the lubricant oil in each back pressure chamber 41 obtains relatively large.
On the other hand, as shown in figure 12, in the time that the rotational speed of live axle 57 increases, because the centrifugal force acting on ball valve body 59 increases, therefore ball valve body 59 against the pushing force of coil spring 61 from the position adjacent with the axes O of live axle 57 nose motion towards guide hole 57C.Reduce gradually towards radial hole 57B from axial bore 57A because guide hole 57C is formed as making its diameter, the net sectional area of the net sectional area that therefore fluid between axial bore 57A and guide hole 57C is communicated with or the connection of rotating channel is along with ball valve body 59 reduces gradually towards the nose motion of guide hole 57C.Therefore,, in the time that the rotational speed of live axle 57 increases, the amount that flow into the lubricant oil in each back pressure chamber 41 reduces.
In the rotary vane compressor of present embodiment, intermittently means of communication 102 works in the mode identical with means of communication 100 the situation at intermittence of the first mode of execution.
Coordinate, in the rotary vane compressor of the present embodiment that forms rotating channel, easily in live axle 57, to form rotating channel at axial bore 57A, radial hole 57B and guide hole 57C.Other effects of the 3rd mode of execution and other effects of the first mode of execution are basic identical.
With reference to Figure 13 and Figure 14, the rotary vane compressor of the 4th mode of execution comprises the live axle 7 of rotary vane compressor and the live axle 63 of back pressure applying mechanism 13A and the back pressure applying mechanism 13D that substitute the first mode of execution.
Live axle 63 has guide hole 63A and radial hole 63B.Guide hole 63A is as axial bore of the present invention.Guide hole 63A and radial hole 63B coordinate to form rotating channel of the present invention.Live axle 63 also has the first peripheral surface 63C and the second peripheral surface (not shown).The first peripheral surface 63C is as peripheral surface of the present invention.
Guide hole 63A is formed as extending forward along the axes O of live axle 63 from the rear end surface of live axle 63 in live axle 63.Guide hole 63A locates to lead to communication chamber 39 in its back-end.Guide hole 63A has the diameter larger than radial hole 63B.Radial hole 63B extends perpendicular to guide hole 63A and opens wide at the first peripheral surface 63C place.Radial hole 63B is communicated with in the position adjacent with the front end of guide hole 63A with guide hole 63A.
In guide hole 63A, be provided with centrifugal valve body 65 and coil spring 67.Centrifugal valve body 65 and coil spring 67 are used separately as valve body of the present invention and pushing member.Guide hole 63A, centrifugal valve body 65 and coil spring 67 coordinate to form control valve unit of the present invention.
Centrifugal valve body 65 has the first lobe plate 65A, the second lobe plate 65B, stationary part 65C, the first motion parts 65D and the second motion parts 65E.As shown in Figure 13 and Figure 14, the cross section of the first lobe plate 65A and the second lobe plate 65B is roughly triangular in shape and have respectively an inclined surface 651 and 652.It is adjacent with the front end of guide hole 63A that lobe plate 65A and 65B are positioned to.Stationary part 65C has the vertical wall 653 extending along the radial direction of live axle 63 and the horizontal wall 654 of extending along the axial direction of live axle 63.Stationary part 65C has the passage 65F forming through its vertical wall 653 and horizontal wall 654.Stationary part 65C locates to be fixed to guide hole 63A in its back-end.As shown in Figure 13 and Figure 14, the cross section of the first motion parts 65D and the second motion parts 65E is trapezoidal and has respectively inclined surface 655 and 656.The inclined surface 655 and 656 of the first motion parts 65D and the second motion parts 65E is positioned to parallel with 652 with the inclined surface 651 of the first lobe plate 65A and the second lobe plate 65B respectively.Motion parts 65D and 65E in guide hole 63A between lobe plate 65A, 65B and stationary part 65C and cross horizontal wall 654.
Coil spring 67 is between the front end and lobe plate 65A, 65B of guide hole 63A, for rear end pushing lobe plate 65A, 65B towards guide hole 63A.
In the rotary vane compressor of present embodiment, guide hole 63A, radial hole 63B and passage 65F allow being communicated with between upstream passageway 5D and communication chamber 39., guide hole 63A, radial hole 63B and passage 65F allow being communicated with between discharge chamber 29 and each supply hole 5E.Guide hole 63A, radial hole 63B, passage 65F, communication chamber 39, upstream passageway 5D and supply hole 5E coordinate to form intermittently means of communication 103.
Upstream passageway 5D, guide hole 63A, radial hole 63B, passage 65F, communication chamber 39, supply hole 5E and oily recess 5F coordinate to form back pressure passage 203.
Back pressure passage 203, guide hole 63A, centrifugal valve body 65, coil spring 67 and intermittently means of communication 103 coordinate to form back pressure applying mechanism 13D.All the other structures of the 4th mode of execution and the counter structure of the first mode of execution are basic identical.
In the rotary vane compressor of present embodiment, the lubricant oil in upstream passageway 5D flow in communication chamber 39 by radial hole 63B, guide hole 63A and passage 65F successively.In the time that live axle 63 rotates, the centrifugal action producing by the rotation of live axle 63 is on centrifugal valve body 65.As shown in Figure 13 and Figure 14, the first lobe plate 65A and the second lobe plate 65B and the first motion parts 65D and the second motion parts 65E move in guide hole 63A.
Particularly, as shown in figure 13, in the time that the rotational speed of live axle 63 is relatively low, owing to now acting on, centrifugal force on the first motion parts 65D and the second motion parts 65E of centrifugal valve body 65 is relatively little, and therefore the first motion parts 65D and the second motion parts 65E are positioned adjacent to the axes O of live axle 63.The pushing force of coil spring 67 makes the first lobe plate 65A and the second lobe plate 65B move along the inclined surface 655,656 of the first motion parts 65D and the second motion parts 65E respectively towards the rear end of guide hole 63A.Therefore the net sectional area that, the fluid between guide hole 63A and radial hole 63B is communicated with becomes relatively large.Therefore the quantitative change that, flow into the lubricant oil in each back pressure chamber 41 obtains relatively large.
On the other hand, as shown in figure 14, in the time that the rotational speed of live axle 63 increases, because the centrifugal force now acting on the first motion parts 65D and the second motion parts 65E of centrifugal valve body 65 increases, therefore the first motion parts 65D and the second motion parts 65E away from each other or away from the position adjacent with the axes O of live axle 63 respectively along inclined surface 651,652 radial motions of the first lobe plate 65A and the second lobe plate 65B.Motion parts 65D and 65E away from the motion of the position adjacent with axes O make lobe plate 65A and 65B against the pushing force of coil spring 67 nose motion towards guide hole 63A.Therefore, the net sectional area being communicated with between guide hole 63A and radial hole 63B reduces gradually.Therefore,, in the time that the rotational speed of live axle 63 increases, the amount that flow into the lubricant oil in each back pressure chamber 41 reduces.It should be pointed out that according to the rotational speed of live axle 63, being communicated with between guide hole 63A and radial hole 63B is cut off, or the useful area being communicated with between guide hole 63A and radial hole 63B is decreased to zero.
In the rotary vane compressor of present embodiment, intermittently means of communication 103 works in the mode identical with means of communication 100 the situation at intermittence of the first mode of execution.Other effects of the 4th mode of execution and other effects of the first mode of execution are basic identical.
With reference to Figure 15, the rotary vane compressor of the 5th mode of execution comprises the live axle 7 of rotary vane compressor and the live axle 69 of back pressure applying mechanism 13A and the back pressure applying mechanism 13E that substitute the first mode of execution.
Live axle 69 has axial bore 69A, radial hole 69B and guide hole 69C.Axial bore 69A and radial hole 69B coordinate to form rotating channel of the present invention.Live axle 69 also has the first peripheral surface 69D and the second peripheral surface (not shown).The first peripheral surface 69D is as peripheral surface of the present invention.
Axial bore 69A is formed as extending forward along the axes O of live axle 69 from the rear end surface of live axle 69 in live axle 69.Axial bore 69A in its back-end surface leads to communication chamber 39.Radial hole 69B hole 69A perpendicular to axial direction extends and opens wide at the first peripheral surface 69D place.Radial hole 69B is communicated with axial bore 69A in the position adjacent with the front end of axial bore 69A.Guide hole 69C hole 69A perpendicular to axial direction radially extends through live axle 69 so that axial bore 69A is divided into front hole and metapore.Guide hole 69C is communicated with axial bore 69A in the position adjacent with the rear end of axial bore 69A.In guide hole 69C, be formed with spring seat 69E.
Bobbin 49 and coil spring 51 are arranged in guide hole 69C.Guide hole 69C, bobbin 49 and coil spring 51 coordinate to form control valve unit of the present invention.
A pair of back-up ring 62B and 62C are engaged in live axle 69 regularly, and a part of back-up ring 62B and 62C is extend in guide hole 69C.Back-up ring 62B respectively with the head 49A of bobbin 49 with seat portion 49D contacts limit bobbin 49 motion among guide hole 49Cs by back-up ring 62B with 62C with 62C.
In the rotary vane compressor of present embodiment, axial bore 69A, radial hole 69B and passage 49E allow between upstream passageway 5D and communication chamber 39 and therefore allow being communicated with between discharge chamber 29 and each supply hole 5E.Axial bore 69A, radial hole 69B, passage 49E, communication chamber 39, upstream passageway 5D and supply hole 5E coordinate to form intermittently means of communication 104.
Upstream passageway 5D, axial bore 69A, radial hole 69B, passage 49E, communication chamber 39, supply hole 5E and oily recess 5F coordinate to form back pressure passage 204.
Back pressure passage 204, guide hole 69C, bobbin 49, coil spring 51 and intermittently means of communication 104 coordinate to form back pressure applying mechanism 13E.All the other structures of the 5th mode of execution and the counter structure of the first mode of execution are basic identical.
In the rotary vane compressor of present embodiment, the lubricant oil in the upstream passageway 5D successively metapore of front hole, passage 49E and the axial bore 69A by radial hole 69B, axial bore 69A flow in communication chamber 39.In the time that live axle 69 rotates, identical with the situation of the first mode of execution, bobbin 49 moves under the impact of centrifugal force in guide hole 69C.
In the time that the rotational speed of live axle 69 is relatively low, the front hole of axial bore 69A and metapore be communicated with passage 49E and axial bore 69A and passage 49E between the net sectional area that is communicated with of fluid relatively large.Therefore, the net sectional area of the connection of the net sectional area being communicated with between axial bore 69A and passage 49E or rotating channel is relatively large.Therefore, flow into the amount of the lubricant oil in each back pressure chamber 41 relatively large.On the other hand, in the time that the rotational speed of live axle 69 increases, the net sectional area of the net sectional area being communicated with between axial bore 69A and passage 49E or the connection of rotating channel reduces gradually.Therefore the amount that, flow into the lubricant oil in each back pressure chamber 41 reduces along with the increase of the rotational speed of live axle 69.
In the rotary vane compressor of present embodiment, intermittently means of communication 104 works in the mode identical with means of communication 100 the situation at intermittence of the first mode of execution.Other effects of the 5th mode of execution and other effects of the first mode of execution are basic identical.
The rotary vane compressor of present embodiment is manufactured more simply than the rotary vane compressor of the first mode of execution and has therefore further reduced manufacture cost in structure aspects.
With reference to Figure 16, the rotary vane compressor of the 6th mode of execution comprises the back pressure applying mechanism 13A of rotary vane compressor and the back pressure applying mechanism 13F of back side panel 5 and the back side panel 71 that substitute the first mode of execution.
Identical with the situation of back side panel 5, back side panel 71 is fixed in the second shell space 17A of rear case 17.Back side panel 71 has boss 71A and cylindrical bearing surface 71B.Boss 71A extends back from the central part of the rear surface 71G of back side panel 71.Although omitted the diagram of the end frame 35 of centrifugal separator 33 in figure, the end frame 35 of centrifugal separator 33 is engaged to the rear surface 71G of back side panel 71, thereby forms communication chamber 39 between end frame 35 and the rear surface 71G of back side panel 71.
Back side panel 71 has upstream passageway 71C, supplies with groove 71D, a pair of supply hole 71E and a pair of oily recess 71F.Upstream passageway 71C vertically extends in back side panel 71.Upstream passageway 71C locates to lead to supply groove 71D in the top.Although do not illustrate in the drawings, upstream passageway 71C leads to discharge chamber 29 at its lower end.Supplying with groove 71D is formed as the annular shape coaxial with bearing surface 71B and extends along the first peripheral surface 7D of live axle 7.Supply hole 71E extends axially towards the front surface of back side panel 71 from the rear end of boss 71A.The oily recess 71F of the 6th mode of execution has the essentially identical structure of oily recess 5F with the first mode of execution.
Upstream passageway 71C, supply groove 71D, radial hole 7B, central hole 7A, putting chamber 7C, communicating passage 47A, passage 49E, communication chamber 39, supply hole 71E and oily recess 71F coordinate to form back pressure passage 205.
Back pressure passage 205, putting chamber 7C and clack box 47 coordinate to form back pressure applying mechanism 13F.All the other structures of the 6th mode of execution and the counter structure of the first mode of execution are basic identical.
Lubricant oil in discharge chamber 29 is flow into and is supplied with in groove 71D by upstream passageway 71C.Being formed as annular shape allows supply groove 71D to be communicated with radial hole 7B in any position of radial hole 7B with the supply groove 71D extending along the first peripheral surface 7D of live axle 7.Therefore, the lubricant oil of supplying with in groove 71D flow in communication chamber 39 constantly by radial hole 7B, central hole 7A, communicating passage 47A and passage 49E, and therefore flow in each back pressure chamber 41.
,, in the rotary vane compressor of present embodiment, only flowing into the amount of the lubricant oil each back pressure chamber 41 from discharge chamber 29 can be adjusted according to the rotational speed of live axle 7.Other effects of the 6th mode of execution and other effects of the first mode of execution are basic identical.
Although described the present invention in the context of the first mode of execution to the six mode of executions, be apparent that to those skilled in the art, in the situation that not deviating from scope of the present invention, can put into practice in every way the present invention.
In the rotary vane compressor of the first mode of execution, bobbin 49 can be formed as making the rotational speed according to live axle 7, being communicated with between communicating passage 47A and passage 49E is cut off, or the net sectional area that fluid between communicating passage 47A and passage 49E is communicated with is reduced to zero.Also be like this for the rotary vane compressor of the 5th mode of execution.In the rotary vane compressor of the 4th mode of execution, centrifugal valve body 65 can be formed as making guaranteeing in the situation that motion parts 65D and 65E move to farthest away from each other the predetermined net sectional area that the fluid between guide hole 63A and radial hole 63B is communicated with.
In the rotary vane compressor of the 4th mode of execution, the first lobe plate 65A and the second lobe plate 65B can be formed as making guaranteeing the predetermined net sectional area being communicated with between guide hole 63A and radial hole 63B when maximum when acting on centrifugal force on centrifugal valve body 65.
The rotary vane compressor of the first mode of execution to the five mode of executions can save respectively intermittently means of communication 100 to 104.
In the rotary vane compressor of the first mode of execution, sliding layer can be by zinc-plated formation on the first peripheral surface 7D at live axle 7 and the second peripheral surface 7E, to substitute sliding layer 27A and the 27B on bearing surface 3B and 5C.Also be like this for the 3rd mode of execution to the five mode of executions.
Claims (6)
1. a rotary vane compressor, comprising:
There is the housing (15,17,19) of suction chamber (25) and discharge chamber (29);
A pair of front side plate and back side panel (3,5,55,71), described a pair of front side plate and back side panel (3,5,55,71) are arranged in described housing (15,17,19) regularly to form rotor chamber (19A) between described a pair of front side plate and back side panel (3,5,55,71);
Live axle (7,57,63,69), described live axle (7,57,63,69) is rotatably bearing in described housing (15,17,19) and extends through described rotor chamber (19A);
Rotor (9), described rotor (9) be arranged in described rotor chamber (19A) and can with described live axle (7,57,63,69) synchronous rotary, described rotor (9) has multiple blade grooves (9A);
Multiple blades (11), described multiple blade (11) is slidably received in corresponding described blade groove (9A) to form multiple back pressure chambers (41), wherein, described blade (11) coordinates to form multiple pressing chambers (43) with the interior perimeter surface of described rotor chamber (19A), the outer surface of described rotor (9), described front side plate (3) and described back side panel (5,55,71); And
Back pressure applying mechanism (13A-13F), described back pressure applying mechanism (13A-13F) by the pressure in described discharge chamber (29) be applied in described back pressure chamber (41) at least one back pressure chamber of the described pressing chamber (43) in compression stage at that time, wherein, described back pressure applying mechanism (13A-13F) comprises back pressure passage (200-205) and control valve unit (47, 49, 51, 57C, 59, 61, 63A, 65, 67, 69C), wherein, described back pressure passage (200-205) allows described discharge chamber (29) to be communicated with each back pressure chamber (41), wherein, described control valve unit (47, 49, 51, 57C, 59, 61, 63A, 65, 67, 69C) be arranged in described back pressure passage (200-205),
Described rotary vane compressor is characterised in that,
Described back pressure passage (200-205) has and is formed on described live axle (7, 57, 63, 69) rotating channel (7A in, 7B, 57A, 57B, 57C, 63A, 63B, 69A, 69B), wherein, described control valve unit (47, 49, 51, 57C, 59, 61, 63A, 65, 67, 69C) comprise and be arranged on described live axle (7, 57, 63, 69) in with described live axle (7, 57, 63, 69) valve body (49 of synchronous rotary, 59, 65), wherein, described valve body (49, 59, 65) be configured at described live axle (7, 57, 63, 69) in the situation that rotational speed increases, reduce described rotating channel (7A, 7B, 57A, 57B, 57C, 63A, 63B, 69A, the net sectional area that fluid 69B) is communicated with.
2. rotary vane compressor according to claim 1, it is characterized in that, described back pressure applying mechanism (13A-13F) comprises intermittently means of communication (100-104), and described means of communication at intermittence (100-104) makes described rotating channel (7A, 7B, 57A, 57B, 57C, 63A, 63B, 69A, 69B) intermittently be communicated with described discharge chamber (29) and each back pressure chamber (41) according to the angular orientation of described live axle (7,57,63,69).
3. rotary vane compressor according to claim 2, it is characterized in that, described rotating channel (7A, 7B, 57A, 57B, 57C, 63A, 63B, 69A, 69B) there is axial bore (63A) and radial hole (63B), described axial bore (63A) extends along the axial direction of described live axle (63), described radial hole (63B) extends and opens wide in the peripheral surface (63C) of described live axle (63) from described axial bore (63A) along the radial direction of described live axle (63), wherein, in described axial bore (63A), there is described valve body (65), and described radial hole (63B) forms a part for described means of communication at intermittence (103).
4. according to the rotary vane compressor described in any one in claims 1 to 3, it is characterized in that, described control valve unit (47, 49, 51, 57C, 59, 61, 63A, 65, 67, 69C) comprise guide hole (47B, 57C, 63A, 69C) with pushing member (51, 61, 67), wherein, described guide hole (47B, 57C, 63A, 69C) be formed on described live axle (7, 57, 63, 69) in and with described rotating channel (7A, 7B, 57A, 57B, 57C, 63A, 63B, 69A, 69B) be communicated with to receive described valve body (49, 59, 65), wherein, described pushing member (51, 61, 67) push described valve body (49 along the direction of the net sectional area that increases fluid connection, 59, 65).
5. rotary vane compressor according to claim 4, it is characterized in that, described control valve unit (47,49,51,57C, 59,61,63A, 65,67,69C) comprises the clack box (47) with described guide hole (47B), wherein, described pushing member (51) is positioned between described clack box (47) and described valve body (49), wherein, described clack box (47) is arranged in the rearward end of described live axle (7).
6. rotary vane compressor according to claim 5, it is characterized in that, described live axle (7) has putting chamber (7C) described in it in rearward end, described clack box (47) is arranged in described putting chamber (7C), wherein, described guide hole (47B) at its end opposite place by the inner surfaces enclose of described putting chamber (7C), thereby limit the motion of described valve body (49).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013070600A JP6171482B2 (en) | 2013-03-28 | 2013-03-28 | Vane type compressor |
| JP2013-070600 | 2013-03-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104074761A true CN104074761A (en) | 2014-10-01 |
| CN104074761B CN104074761B (en) | 2016-02-10 |
Family
ID=51596283
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410120047.1A Expired - Fee Related CN104074761B (en) | 2013-03-28 | 2014-03-27 | Rotary vane compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6171482B2 (en) |
| CN (1) | CN104074761B (en) |
| BR (1) | BR102014007311A2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106014984A (en) * | 2016-05-25 | 2016-10-12 | 洛阳普瑞曼自动控制技术有限公司 | Distributed automatic-compensation vane vacuum pump |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5718796U (en) * | 1980-07-04 | 1982-01-30 | ||
| US4834634A (en) * | 1987-06-24 | 1989-05-30 | Diesel Kiki Co., Ltd. | Sliding-vane rotary compressor for bearing lubrication |
| JPH07151083A (en) * | 1993-11-29 | 1995-06-13 | Nippondenso Co Ltd | Vane type compressor |
| US5499515A (en) * | 1993-06-23 | 1996-03-19 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Rotary vane-type compressor |
| JP2001165082A (en) * | 1999-12-13 | 2001-06-19 | Matsushita Electric Ind Co Ltd | Sliding vane type compressor |
| CN102477981A (en) * | 2010-11-24 | 2012-05-30 | 株式会社丰田自动织机 | Blade-type compressor |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6348985U (en) * | 1986-09-18 | 1988-04-02 | ||
| JPH01105788U (en) * | 1988-01-06 | 1989-07-17 | ||
| JPH01125880U (en) * | 1988-02-22 | 1989-08-28 | ||
| JP2003113787A (en) * | 2001-10-03 | 2003-04-18 | Seiko Instruments Inc | Gas compressor |
| JP5659964B2 (en) * | 2010-11-24 | 2015-01-28 | 株式会社豊田自動織機 | Vane type compressor |
-
2013
- 2013-03-28 JP JP2013070600A patent/JP6171482B2/en not_active Expired - Fee Related
-
2014
- 2014-03-27 CN CN201410120047.1A patent/CN104074761B/en not_active Expired - Fee Related
- 2014-03-27 BR BR102014007311A patent/BR102014007311A2/en not_active IP Right Cessation
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5718796U (en) * | 1980-07-04 | 1982-01-30 | ||
| US4834634A (en) * | 1987-06-24 | 1989-05-30 | Diesel Kiki Co., Ltd. | Sliding-vane rotary compressor for bearing lubrication |
| US5499515A (en) * | 1993-06-23 | 1996-03-19 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Rotary vane-type compressor |
| JPH07151083A (en) * | 1993-11-29 | 1995-06-13 | Nippondenso Co Ltd | Vane type compressor |
| JP2001165082A (en) * | 1999-12-13 | 2001-06-19 | Matsushita Electric Ind Co Ltd | Sliding vane type compressor |
| CN102477981A (en) * | 2010-11-24 | 2012-05-30 | 株式会社丰田自动织机 | Blade-type compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014194177A (en) | 2014-10-09 |
| JP6171482B2 (en) | 2017-08-02 |
| CN104074761B (en) | 2016-02-10 |
| BR102014007311A2 (en) | 2014-12-23 |
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