CN102052318A - Compressor - Google Patents

Compressor Download PDF

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Publication number
CN102052318A
CN102052318A CN2010105225431A CN201010522543A CN102052318A CN 102052318 A CN102052318 A CN 102052318A CN 2010105225431 A CN2010105225431 A CN 2010105225431A CN 201010522543 A CN201010522543 A CN 201010522543A CN 102052318 A CN102052318 A CN 102052318A
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CN
China
Prior art keywords
operating chamber
inner peripheral
peripheral surface
side operating
upstream side
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Pending
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CN2010105225431A
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Chinese (zh)
Inventor
稻垣章
石原孝宏
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Denso Corp
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Denso Corp
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Publication date
Priority claimed from JP2010089512A external-priority patent/JP5273085B2/en
Application filed by Denso Corp filed Critical Denso Corp
Publication of CN102052318A publication Critical patent/CN102052318A/en
Pending legal-status Critical Current

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Abstract

The invention provides a compressor, which comprises a plurality of sets of housings (10), disc-shaped rotary plungers (31, 32) and blades (51, 52).Inner circumferential surfaces (101b, 102b) with circular sections are formed by the housings.The plungers (31, 32) eccentrically rotate along the inner circumferential surfaces.The blades (51, 52) emerge from the inner circumferential surfaces and abut against the rotary plungers.An inhalation stroke for inhaling fluid is performed and the inhaled fluid is compressed in operation chambers (41, 42) arranged between the inner circumferential surfaces and the rotary plungers.The rotary phase of one of the rotary plungers is further forward than that of other rotary plungers.When an operation chamber formed by the rotary plunger with a further forward rotary phase is served as an upstream operation chamber, a discharge path (105a) is formed on the housing.The fluid is compressed in other operation chambers by the discharge path during the period from the formation of the upstream operation chamber to the end of the inhalation stroke.

Description

Compressor
Technical field
The present invention relates to a kind of compressor with a plurality of cylinders.
Background technique
At present, as this compressor, the axial upward alignment arrangements that has patent documentation 1 (TOHKEMY 2005-127306 communique) to put down in writing has rotary plunger formula (the rolling piston type) compressor of two cylinders.At this, so-called rotary plunger formula compressor is meant: dispose rotary plunger in the cylinder that forms the toroidal inner peripheral surface, come convection cell to carry out compressor for compressing by rotary plunger along the eccentric rotation of the inner peripheral surface of cylinder.
In patent documentation 1, two separate actions of cylinder.That is, be respectively equipped with suction port and ejiction opening on two cylinders, compressed refrigerant sucks each cylinder in order to incite somebody to action not from suction port, and from ejiction opening ejection compressed refrigerant, makes each cylinder with respect to refrigerator stream side by side.
According to this documents 1, owing to, therefore the change of shaft torque can be suppressed lower with two cylinder compressed refrigerants.That is, by the phase place that staggers between two cylinders, and cylinder identical with total capacity only has one rotary plunger formula compressor to compare, and the change of shaft torque can be suppressed lower.At this, shaft torque is meant and is used for driving the needed torque of axle that links with rotary plunger.
But, as above-mentioned prior art, iff being that two cylinders that phase place is different are set up in parallel merely, then because the change characteristic of the shaft torque of each cylinder in a disguised form together, therefore can produce the peak value of shaft torque in each action cycle of each cylinder.
Specifically, to compare with the situation that a cylinder is only arranged be its twice to the generation frequency of the peak value of shaft torque.Therefore, because the variation frequency of shaft torque uprises, so misgivings with miscellaneous part resonance are arranged.
For example, be applicable under the situation of vehicle with the compressor of refrigeration cycle, might with compressor together with the resonance such as various subsidiary engines that are disposed at engine compartment.
And this problem does not exist only in rotary plunger formula compressor, and can produce too in revolution type compressors such as yoke chip (yoke vanetype) compressor.At this, so-called yoke chip compressor is meant: the rotor that connects the layout circle shape in the cylinder of the inner peripheral surface with toroidal, disposing tabular blade (vane) makes in its slit that can form on rotor and haunts, be connected at blade under the state of cylinder inner peripheral surface, rotor is around its central shaft rotation, and convection cell carries out compressor for compressing thus.So-called revolution type compressor is meant: configuration rotary component and zoning parts in the cylinder of the inner peripheral surface with regulation shape, the operating chamber convection cell that forms between inner peripheral surface and rotary component and zoning parts carries out compressor for compressing.
Summary of the invention
The present invention proposes in view of above-mentioned point, and purpose is to take into account simultaneously the low torque change and hangs down variation frequency.
In order to reach above-mentioned purpose, the present invention's first example is a kind of compressor, it is characterized in that,
It possesses many group inner peripheral surfaces and forms parts, rotary component and division parts, described inner peripheral surface forms the inner peripheral surface that parts form the regulation shape, described rotary component and described inner peripheral surface join and rotate, described division parts are divided the space that forms between described inner peripheral surface and described rotary component
In described inner peripheral surface forms parts between each described inner peripheral surface and described rotary component and the described division parts, formation sucks the suction stroke of fluid and the operating chamber of compression stroke that the described fluid by described suction stroke suction is compressed,
A rotary component among a plurality of described rotary components is more forward than the rotatable phase of other described rotary component,
The operating chamber that is formed by a described rotary component among with a plurality of described operating chamber is during as the upstream side operating chamber, form on the parts at described inner peripheral surface and to be formed with the ejection path, other operating chamber described ejection path compresses described fluid after described suction stroke is finished among described upstream side operating chamber is formed into a plurality of described operating chamber.
In view of the above, because by a plurality of operating chamber compressed fluids, so the change of shaft torque can be suppressed less.And, because compressed fluid moves in other operating chamber associations that lag behind with forward upstream side operating chamber of rotatable phase and rotatable phase, so can make the change characteristic difference of the shaft torque in each operating chamber.Therefore, can suppress the generation of the peak value of the shaft torque in the synthetic shaft torque, thereby can realize the low torque change and hang down take into account (with reference to Fig. 5 described later and Fig. 6) of variation frequency.
For example, when with other operating chamber during as the downstream side operating chamber, compressor can possess the mechanism that forces down sealing ejection path under the situation of the interior pressure of downstream side operating chamber in the upstream side operating chamber.
Thus, the refrigeration agent that can prevent the downstream side operating chamber arrives the upstream side operating chamber by ejection path adverse current.
And then, in above-mentioned compressor, can also be upstream side operating chamber and downstream side operating chamber the upstream side operating chamber axially on disposed adjacent, inner peripheral surface forms parts and has the tabular separating part of separating upstream side operating chamber and downstream side operating chamber, the ejection path is formed at separating part.At this moment, the mechanism of sealing ejection path can be made of rotary component.
In view of the above, the situation that is specifically designed to the mechanism of sealing ejection path with setting is compared, can simplified structure.
In above-mentioned arbitrary compressor, the cross section that can be inner peripheral surface is for circular, and rotary component is the discoid rotary plunger along the eccentric rotation of inner peripheral surface, divides parts and is from inner peripheral surface and haunt and be connected to the blade of rotary plunger.
Thus, in rotary plunger formula compressor, can obtain the effect of above-mentioned invention.
Perhaps, in compressor, the cross section of described inner peripheral surface can be circle.At this moment, rotary component is the discoid rotary plunger along the eccentric rotation of inner peripheral surface, divide parts and be from inner peripheral surface and haunt and be connected to the blade of rotary plunger, upstream side operating chamber and downstream side operating chamber the upstream side operating chamber axially on disposed adjacent, inner peripheral surface forms parts and has the tabular separating part of separating upstream side operating chamber and downstream side operating chamber, the ejection path is formed at separating part, the end of upstream side operating chamber side and the end of downstream side operating chamber side among the ejection path are with respect to the opening scope difference of separating part.
And then, in compressor, can be that the slot part that extends along the plate face of separating part from the end of upstream side operating chamber among the through hole portion that extended in parallel by the thickness direction with respect to separating part of ejection path and the through hole portion constitutes.
In view of the above, for example compare with the situation that is made of the ejection path the hole portion with respect to the thickness direction diagonally extending of separating part, the ejection path carries out with respect to the easy processing of separating part.
Perhaps, in compressor, the cross section that can be inner peripheral surface is for circular, and rotary component is connected to inner peripheral surface and rotor rotated in being, divides parts and is from the outer circumferential face of rotor and haunt and be connected to the blade of inner peripheral surface.
Thus, even in this yoke chip compressor, also can obtain the effect of above-mentioned invention.
Perhaps, in compressor, the cross section that can be inner peripheral surface is for circular, and rotary component is connected to inner peripheral surface and rotor rotated in being, divides parts and is from the outer circumferential face of rotor and haunt and be connected to the blade of inner peripheral surface.
At this moment, can be upstream side operating chamber and downstream side operating chamber the upstream side operating chamber axially on disposed adjacent, inner peripheral surface forms parts and has the tabular separating part of separating upstream side operating chamber and downstream side operating chamber, the ejection path is formed at separating part, the end of upstream side operating chamber side overlaps with the rotor that forms the upstream side operating chamber among the ejection path, the end of downstream side operating chamber side overlaps with the rotor that forms the downstream side operating chamber among the ejection path, on the rotor that forms the upstream side operating chamber, be formed with the upstream side access that the ejection path is communicated with the upstream side operating chamber, on the rotor that forms the downstream side operating chamber, be formed with the downstream side access that the ejection path is communicated with the downstream side operating chamber.
Thus, even in yoke chip compressor, also can obtain the effect of above-mentioned invention.
And then the upstream side access can be made of the groove that forms at the end face of separating part side among the rotor that forms the upstream side operating chamber, and the downstream side access can be made of the groove that forms at the end face of separating part side among the rotor that forms the downstream side operating chamber.
Thus, access carries out with respect to the easy processing of rotor.
In above-mentioned arbitrary compressor, with other operating chamber during as the downstream side operating chamber, the maximum volume of downstream side operating chamber is less than the maximum volume of upstream side operating chamber.
Thus,, press the characteristic optimization in can making, further reduce cogging by the volume of suitable each operating chamber of setting.
Perhaps, the rotary component that forms a plurality of operating chamber is constituted as the mutual non-equalization of rotatable phase difference.
So,, press the characteristic optimization in can making, further reduce cogging by the phase difference of suitable each operating chamber of setting.
In addition, in the present invention, with the number of operating chamber, be that the number of rotary component is when being made as n, the mutual rotatable phase difference of rotary component is set under the situation of value of 360 °/n and is called " the rotatable phase difference equalization that rotary component is mutual ", is called " the non-equalization of rotatable phase difference that rotary component is mutual " under the situation that is set at the value that is different from 360 °/n.
Description of drawings
Fig. 1 is the ideograph of the vehicle of first mode of execution with refrigeration cycle;
Fig. 2 is the sectional view of the compressor of first mode of execution;
Fig. 3 is the explanatory drawing that the structure to the ejection path that opens and closes Fig. 2 describes;
Fig. 4 (a) is the B-B sectional view of Fig. 3, and Fig. 4 (b) is the C-C sectional view of Fig. 3;
Fig. 5 is the coordinate diagram of pressure and the variation of chamber capacity in the chamber of expression first mode of execution;
Fig. 6 is the coordinate diagram of variation of the shaft torque of expression first mode of execution;
Fig. 7 is the explanatory drawing that the structure to the ejection path that opens and closes second mode of execution describes;
Fig. 8 is the sectional view of the compressor of the 3rd mode of execution;
Fig. 9 is the sectional view of the compressor of the 4th mode of execution;
Figure 10 is the sectional view of the compressor of the 5th mode of execution;
Figure 11 is the explanatory drawing that the structure to the ejection path that opens and closes Figure 10 describes;
Figure 12 (a) is the F-F sectional view of Figure 11, and Figure 12 (b) is the G-G sectional view of Figure 11;
Figure 13 is the coordinate diagram of the variation of pressure in the chamber of expression the 5th mode of execution, chamber capacity and shaft torque;
Figure 14 is the sectional view of the compressor of the 6th mode of execution;
Figure 15 is the sectional view of the compressor of the 7th mode of execution.
Embodiment
(first mode of execution)
Below, based on Fig. 1～Fig. 6 first mode of execution of the present invention is described.Fig. 1 is suitable for the ideograph of the vehicle of compressor of the present invention with refrigeration cycle.
Compressor (compressor) 1 sucks refrigeration agent (fluid) and ejection.Condenser (radiator) 2 makes from the vapor phase refrigerant condensation of compressor 1 ejection.3 pairs of refrigeration agents that flow out from condenser 2 of decompressor reduce pressure.As decompressor, vaporizer 4 makes the liquid phase refrigerant evaporation of having been reduced pressure by decompressor 3.The vapor phase refrigerant that flows out from vaporizer 4 is inhaled into compressor 1.
Fig. 2 (a) is the sectional view of compressor 1.Fig. 2 (b) is the A-A sectional view of Fig. 2 (a).Compressor 1 is the rotary plunger formula compressor of three cylinders, and has shell 10 (inner peripheral surface formation parts) 10 that forms cylinder and the axle 11 that is inserted in the shell 10.
In the example of Fig. 2, shell 10 be with bolt (not shown) axially (left and right directions of Fig. 2 (a)) go up divided four and cut apart case member 101,102,103,104 and cut apart case member 101,102,103,104 three demarcation strips 105,106,107 each other and carry out fastening fixing and formation with being sandwiched in.Cutting apart case member 101～104 and demarcation strip 105～107 is formed by aluminium.
Cut apart to be disposed in the case member 101～104 at four and be formed with in the axial direction circular port 102a, the 103a that connects cutting apart of axial center side on the case member 102,103.Therefore, cut apart inner peripheral surface 102b, the 103b that case member 102,103 forms cross section toroidal (regulation shape).
With respect to this, be formed with circular depressions 101a on the case member 101 axial one cutting apart of distolateral (Fig. 2 (a) left end side) being disposed at, circular depressions 101a and circular port 102a, the 103a arranged coaxial of cutting apart case member 102,103, and towards the axial the other end (the right-hand member side of Fig. 2 (a)) opening.Therefore, cut apart the inner peripheral surface 101b that case member 101 forms the cross section circle.
Thus, cutting apart between case member 101～103 and the demarcation strip 105～107, series connection forms the space 21,22,23 of three cross section circles in the axial direction.In addition, in the present embodiment, the internal diameter size of three cross section circular spaces 21～23 and volume equate mutually.
Three cross section circular spaces 21～23 constitute the operating chamber 41,42,43 that sucks refrigeration agent and compression.Therefore, demarcation strip 105,106 plays the effect as the separating part of separating three operating chamber 41～43.
Be disposed at axially cutting apart on the case member 104 of another distolateral (the right-hand member side of Fig. 2 (a)) among cutting apart case member 101～104 at four, be formed with recess 104a towards axial one distolateral (left end side of Fig. 2 (a)) opening.
Therefore, cutting apart formation space 24 between case member 104 and the demarcation strip 107.It is the ejection chamber of operating chamber 41～43 refrigerant compressed by ejection cross section circular space 21～23 that this space 24 constitutes ejection.
Axle 11 runs through the central part and the demarcation strip 105～107 of three cross section circular spaces 21～23.The both end sides position of axle 11 can be supported by shell 10 rotatably through bearing 12,13.
Be formed with the hole 101c that is used for an end (left part of Fig. 2 (a)) of axle 11 is linked to a driving mechanism (not shown) on the case member 101 cutting apart.Internal configurations at hole 101c is useful on the lip seal 14 that prevents freezing medium leakage.
In this example, owing to use motor that vehicle driving uses as the axle driving mechanism, so the pulley (not shown) and the magnetic clutch (not shown) of transmission from the driving force of motor arranged in a distolateral binding of axle 11.Can also use electric motor as the axle driving mechanism.
Dispose the discoid rotary plunger (rotary component) 31,32,33 that links with axle 11 respectively at three cross section circular spaces 21～23.
Rotary plunger 31～33 links with axle 11, and the outside dimension of rotary plunger 31～33 is less than the internal diameter size of cross section circular space 21～23, and rotary plunger 31～33 is with respect to 21～23 eccentric rotations of cross section circular space.
And, be connected to inner peripheral surface 101b, 102b, the 103b of cross section circular space 21～23 among the rotary plunger 31～33 from rotating center position (hereinafter referred to as distal part) farthest.Therefore, rotary plunger 31～33 is along the eccentric rotation of inner peripheral surface 101b, 102b, 103b of cross section circular space 21～23.
Between cross section circular space 21～23 and rotary plunger 31～33, form the operating chamber 41,42,43 that sucks refrigeration agent and compress.Below, for convenience of explanation, axial one distolateral operating chamber 41 is called first section operating chamber, the operating chamber 42 of axial central authorities is called second section operating chamber, axial another distolateral operating chamber 43 is called the 3rd section operating chamber.
In the present embodiment, the boundary dimension of rotary plunger 31～33 is identical mutually.In addition, in the present embodiment, three rotary plungers 31～33 link with axle 11 according to the mode of mutual rotatable phase difference equalization.That is, rotary plunger 31～33 mutual rotatable phase differences are set to 360 °/3=120 °.
Rotary plunger 31～33 is by constituting with the bottom: rotor part 31a, the 32a, the 33a that are fixed in axle 11; Be disposed at ring- type plunger portion 31b, 32b, the 33b of the outer circumferential side of rotor part 31a, 32a, 33a; And be used for bearing post piston part 31b, 32b, 33b and make it with respect to rotor part 31a, 32a, 33a rotation bearing (not shown) freely.
In addition, rotary plunger 31～33 need not make plunger portion 31b, 32b, 33b constitute with respect to rotor part 31a, 32a, 33a to rotate freely, also plunger portion 31b, 32b, 33b and rotor part 31a, 32a, 33a can be formed one and is made of parts.
Be formed with recess 101d, 102d, the 103d that caves in towards radial outside (upper side among Fig. 2) at inner peripheral surface 101b, 102b, the 103b of cutting apart case member 101～103. Recess 101d, 102d, 103d form the groove shape on the entire axial length of inner peripheral surface 101b, 102b, 103b.
Tabular blade (zoning parts) 51,52,53 (can haunt) slidably and be inserted in recess 101d, 102d, 103d.Dispose the spring 15,16,17 of blade 51～53 being pushed to the central side of cross section circular space 21～23 at recess 101d, 102d, 103d.
Under the thrust of spring 15～17, blade 51～53 haunts from inner peripheral surface 101b, 102b, 103b corresponding to the rotational position of rotary plunger 31～33 and is connected to plunger portion 31b, 32b, the 33b of rotary plunger 31～33.Therefore, operating chamber 41～43 is divided into two spaces by blade 51～53.
Below, for convenience of description, the angle of swing that the distal part of rotary plunger 31～33 is connected to the rotary plunger 31～33 of blade 51～53 o'clock is defined as 0 ° (with reference to figure 3 (a)).
Cutting apart the suction port (not shown) that is formed with the refrigeration agent (not compressed refrigerant) that suction flows out from vaporizer 4 on the case member 101.Shown in Fig. 2 (b), be formed with the suction path 101e that the refrigeration agent that will suck from suction port is supplied to operating chamber 41 cutting apart case member 101.
Suck path 101e at inner peripheral surface 101b opening, and open and close by rotary plunger 31.In this example, represent then in about 30 ° position (with reference to figure 3) with the angle of swing of rotary plunger 31～33 if suck the allocation position of path 101e.
Also be formed with on the case member 102,103 and suck same suction path 102e, the 103e of path 101e cutting apart.Because the allocation position of suction path 102e, 103e and shape etc. are identical with suction path 101e, are labeled in the bracket of Fig. 2 (b) so only will suck the symbol of path 102e, 103e, omit the diagram that sucks path 102e, 103e.
Be formed with the adjacent operating chamber 41,42 of connection ejection path 105a each other at demarcation strip 105.In the present embodiment, be formed with three ejection path 105a.If the allocation position of three ejection path 105a represents with the angle of swing of rotary plunger 31～33, then about 270 °, about 310 °, about 350 ° position (with reference to figure 3).
Same with demarcation strip 105, on demarcation strip 106, also be formed with adjacent operating chamber 42, the 43 ejection path 106a each other of connection.Because the allocation position of ejection path 106a and shape etc. are identical with ejection path 105a, the symbol that therefore only will spray path 106a is labeled in the bracket of Fig. 2 (b), omits the diagram of ejection path 106a.
Ejection path 105a is opened and closed by rotary plunger 31,32.Equally, ejection path 106a is opened and closed by rotary plunger 32,33.Fig. 3 is the explanatory drawing that the structure that is opened and closed ejection path 105a by rotary plunger 31,32 is described, by per 30 ° angle of swing represent rotary plunger 31,32 revolve turn around during action.
Fig. 4 (a) is the B-B sectional view of Fig. 3 (a), and illustrative is the state that is sprayed path 105a by rotary plunger 31,32 sealings.Fig. 4 (b) is the C-C sectional view of Fig. 3 (a), and illustrative is the state of being opened ejection path 105a by rotary plunger 31,32.
In addition, for the structure that opens and closes ejection path 106a, since identical with the structure of Fig. 3, switching ejection path 105a shown in Figure 4, diagram therefore omitted.
Ejection path 105a is with respect to the aperture position (opening scope) of demarcation strip 105, and at one end portion is different with the other end.Specifically, as shown in Figure 4, the plate along demarcation strip 105 constitutes towards the slot part 105c that radial outside extends from the end of first section operating chamber 41 side among the 105b of through hole portion of the circle that extended in parallel by the thickness direction with respect to demarcation strip 105 of ejection path 105a and the 105b of through hole portion.
In Fig. 3, rotary plunger 31～33 rotates to clockwise direction.Below for convenience of explanation, the sense of rotation with rotary plunger 31～33 singly is called sense of rotation.In addition, the angle of swing of rotary plunger 31 is called first section angle of swing, the angle of swing of rotary plunger 32 is called second section angle of swing.
Be that as Fig. 4 (a) illustration, ejection path 105a is closed under the situation of angle of swing=240 °～0 ° of 0 °～120 ° and second section in the angle of swing of first section shown in Fig. 3 (a)～(e).That is, the end (end of slot part 105c side) of ejection path 105a is not though be rotated plunger 31 obstructions, and the other end (end of an opposite side with slot part 105c) of ejection path 105a is rotated plunger 32 and stops up, and therefore, ejection path 105a is closed.
On the other hand, under the situation of angle of swing=30 of angle of swing=150 of first section shown in Fig. 3 (f)～(1) °～330 ° and second section °～210 °, as Fig. 4 (b) illustration, ejection path 105a opens.That is, the two end part of ejection path 105a are not rotated plunger 31,32 and stop up, and therefore spray path 105a and open.
Be formed with the final ejection path (not shown) that is communicated with operating chamber 43 and ejection chamber 24 at the demarcation strip 107 shown in Fig. 2 (a).Dispose the ejection valve (not shown) that opens and closes final ejection path at demarcation strip 107.In the example of Fig. 2, adopt the needle spring plate valve as the ejection valve, dispose the stopper (retainer) 19 of the aperture of restriction ejection valve at demarcation strip 107.The refrigeration agent of ejection chamber 24 is sprayed to condenser 2 from the ejiction opening (not shown) that is formed at shell 10.
Below, the action of said structure is described.When 11 rotations of axle driving mechanism (not shown) live axle, rotary plunger 31～33 eccentric rotations.By the off-centre rotation of rotary plunger 31～33, carry out suction stroke and compression stroke repeatedly in each operating chamber 41～43.
At this, suction stroke is: operating chamber 41～43 is in connected state with suction path 101e, 102e, 103e, is inhaled into the stroke of operating chamber 41～43 from the not compressed refrigerant that sucks path 101e, 102e, 103e.Compression stroke is: operating chamber 41～43 is in non-connected state, the stroke of compressed refrigerant in operating chamber 41～43 with suction path 101e, 102e, 103e.
As mentioned above, operating chamber 41～43 is divided into two spaces by blade 51～53.Suction stroke is carried out in a side space among these two spaces, carries out compression stroke in the opposing party space.
Based on Fig. 3 it is specifically described.At this, only describe for first section operating chamber 41, also identical for second section operating chamber 42 with the 3rd section operating chamber 43 elemental motions.
During in angle of swing ≠ 0 of first section shown in Fig. 3 (b)～(1) °, in two spaces that operating chamber 41 forms, carry out suction stroke, promptly carry out compression stroke in the space that is positioned at sense of rotation opposition side (being rotated counterclockwise the direction side) with respect to blade 51 in another space in the space that is positioned at sense of rotation side (dextrorotation veer side) with respect to blade 51.
One side's of operating chamber 41 space begins suction stroke when becoming connected state with suction path 101e.Then, when becoming non-connected state, path 101e when suction stroke finishes, begins compression stroke in a side's of operating chamber 41 space with sucking.
Compression stroke finishes during in angle of swing=0 of first section shown in Fig. 3 (a) °.That is, when first section angle of swing=0 °,, therefore carry out the volume vanishing in the space of compression stroke, thereby compression stroke finishes because blade 51 is rotated the outside that the distal part of plunger 31 is pressed into operating chamber 41.
So, if be conceived to a space among two spaces of operating chamber 41, axle 11 revolve take two turns during, suction stroke and compression stroke are carried out a circulation.On the other hand, if be conceived to operating chamber 41 integral body, then suction stroke and compression stroke are carried out at two spatial parallelisms of operating chamber 41, therefore, axle 11 revolve turn around during, suction stroke and compression stroke are respectively carried out once.
As mentioned above, be that ejection path 105a opens under 150 °～330 ° the situation in the angle of swing of first section shown in Fig. 3 (f)～(l).Thus, be ejected into second section adjacent operating chamber 42 first section operating chamber 41 refrigerant compressed by ejection path 105a.
As mentioned above, because in second section operating chamber 42, rotatable phase lags behind 120 ° with respect to first section operating chamber 41, and second section angle of swing when therefore spraying path 105a and opening is 30 °～210 °.
Therefore, the space in the compression stroke among two spaces of second section operating chamber 42 (being in the space in the compression after the suction stroke end) supply is by first section operating chamber 41 refrigerant compressed.The result is in second section operating chamber 42, and the compressed refrigerant after being compressed by first section operating chamber 41 is blended in from the not compressed refrigerant that sucks path 102e supply and is compressed.
In second section operating chamber 42, same with first section operating chamber 41, because in angle of swing is that ejection path 106a opens under 150 °～330 ° the situation, therefore the refrigeration agent after 42 compressions of second section operating chamber is ejected into the 3rd section adjacent operating chamber 43 by ejection path 106a.
At this, be that the angle of swing of first section operating chamber 41 is 0 °～90 ° under 240 °～330 ° the situation second section angle of swing.That is, therefore the interior pressure of first section operating chamber 41 became and was lower than the interior pressure of second section operating chamber 42 owing to compression stroke in first section operating chamber 41 finishes to become suction stroke this moment.
At this moment, shown in Fig. 3 (a)～(d), ejection path 105a is closed, and the refrigeration agent that therefore prevents second section operating chamber 42 is by spraying path 105a adverse current to first section operating chamber 41.
Also same in the 3rd section operating chamber 43 with second section operating chamber 42, because the refrigeration agent after the supply of the space in the compression stroke is compressed by second section operating chamber 42 among two spaces, the compressed refrigerant after therefore being compressed by second section operating chamber 42 is blended in from the not compressed refrigerant that sucks path 103e supply and is compressed.
In addition, ejection path 106a is also same with ejection path 105a, seal owing to also in second section operating chamber 42, force down under the situation of the interior pressure of the 3rd section operating chamber 43, the refrigeration agent that therefore prevents the 3rd section operating chamber 43 by ejection path 106a adverse current to second section operating chamber 42.
And when the interior pressure of the 3rd section operating chamber 43 reaches authorized pressure when above, ejection valve (not shown) is opened, and therefore, is ejected into ejection chamber 24 by the refrigeration agent after 43 compressions of the 3rd section operating chamber.
Fig. 5 (a) is the coordinate diagram of pressing the change of (the interior pressure in the space among two spaces of operating chamber in the compression stroke) in the chamber of representing in the above-mentioned action.The angle of swing of the transverse axis of Fig. 5 (a) is represented first section angle of swing.The dotted line of Fig. 5 (a) is a comparative example, and total capacity and the operating chamber identical with present embodiment of expression operating chamber only has the change of pressure in the chamber in the rotary plunger formula compressor of (cylinder).
As mentioned above owing to be set with 120 ° phase difference each other in operating chamber 41～43, therefore each operating chamber 41～43 carry out compression stroke during respectively stagger 120 °.
Therefore, in angle of swing=0 °～120 °, only by first section operating chamber 41 compressed refrigerant; In angle of swing=120 °～240 °, by first section operating chamber 41 and second section operating chamber 42 compressed refrigerant; In angle of swing=240 °～360 °, by first section～the 3rd section operating chamber 41～43 compressed refrigerants; In angle of swing=360 °～480 °, by second section operating chamber 42 and the 3rd section operating chamber 43 compressed refrigerants; In angle of swing=480 °～600 °, only by the 3rd section operating chamber 43 compressed refrigerants.
, same only with comparative example by in angle of swing=0 of first section operating chamber 41 compressed refrigerant °～120 °, press liter in the chamber.
By among angle of swing=120 of first section operating chamber 41 and second section operating chamber 42 compressed refrigerant °～240 °, in angle of swing=120 °～150 °, ejection path 105a does not open yet, and first section operating chamber 41 and second section operating chamber 42 are by isolated.
Therefore, in first section operating chamber 41, rising with crimping in the same chamber of comparative example, on the other hand owing to only be that compressed refrigerant is not compressed second section operating chamber 42, thus second section operating chamber 42 in force down interior pressure in first section operating chamber 41.
Then, in angle of swing=150 °～240 °, ejection path 105a opens, and the interior pressure of the interior pressure of first section operating chamber 41 and second section operating chamber 42 becomes impartial, afterwards first section and second section operating chamber 41,42 in press liter.Therefore, compare with comparative example, the rising of pressing in the chamber slows down slowly.
By among angle of swing=240 of first section～the 3rd section operating chamber 41～43 compressed refrigerants °～360 °, in angle of swing=240 °～270 °, because ejection path 106a does not open yet, therefore the 3rd section operating chamber 43 in force down in the interior pressure of first section and second section operating chamber 41,42.
Then, in angle of swing=270 °～360 °, ejection path 105a opens, the equalization thereby the interior pressure of the interior pressure of first section operating chamber 41, second section operating chamber 42 and the 3rd section operating chamber 43 becomes, afterwards, press liter in first section～the 3rd section operating chamber 41～43.Therefore, compare with comparative example, the rising of pressing in the chamber is slower.
In addition, after angle of swing=about 320 °, the rising of pressing in the chamber stops, and this is because press the valve of opening that reaches ejection valve (not shown) to press (authorized pressure) in the chamber, sprays valve and opens.
From Fig. 5 (a) as can be known, in the present embodiment,, therefore compare at the comparative example of 360 ° of cylinders finishing with compression stroke because compression stroke is finished at 600 ° (360 °+120 °+120 °),, can make the rising of pressing in the chamber slow.Therefore, compare, can reduce cogging significantly, and in the cogging frequency, can make once component (primary components) be principal component (primary coil) with comparative example.At this, it is one-period to produce component once that a so-called component of degree n n is meant with 360 ° of angle of swing (rotary plunger turns around).
Be elaborated for its effect.Fig. 5 (b) is the coordinate diagram by the change of operating chamber 41～43 above-mentioned action lumen capacity of expression (capacity in the space among two spaces of operating chamber in the compression stroke).Fig. 6 (a) is the coordinate diagram by the change of shaft torque in the above-mentioned action of operating chamber 41～43 expressions.Fig. 6 (b) is the coordinate diagram of expression synthetic shaft torque after synthetic with the shaft torque of each operating chamber 41～43 among Fig. 6 (a).
At this, shaft torque is the required torque of live axle 11, with pressing element in the variation of chamber capacity and the chamber relation is arranged.Specifically, press in the variation of chamber capacity and chamber that shaft torque becomes big under the big situation.
Therefore, change characteristic according to the chamber capacity of each operating chamber 41～43 shown in pressure and Fig. 5 (b) in the chamber shown in Fig. 5 (a), can obtain the shaft torque of each operating chamber 41～43 shown in Fig. 6 (a), and then the shaft torque by each operating chamber 41～43 shown in the composite diagram 6 (a), can obtain the synthetic shaft torque shown in Fig. 6 (b).In addition, the dotted line of Fig. 6 (a) and (b) is represented above-mentioned comparative example, i.e. shaft torque in the rotary plunger formula compressor of the total capacity of an operating chamber and cylinder identical with present embodiment.
In the present embodiment, shown in Fig. 6 (a), because the change characteristic of the shaft torque in each operating chamber 41～43 is significantly different mutually, therefore shown in Fig. 6 (b), the change of synthesizing shaft torque can be suppressed less, and in synthetic shaft torque, avoid the compression stroke of each operating chamber 41～43 to produce peak value, the generation of peak value can be suppressed be 360 ° of angle of swing only once.
Therefore, can take into account low torque and change and hang down contrary characteristic in the such prior art of variation frequency.And, by realizing the low torque change, can make the action of compressor 1 smooth and easy, can reduce vibration.In addition, by realizing low variation frequency, can suppress and resonance at the various subsidiary engines of engine compartment configuration etc.
In addition, according to present embodiment, sealing downstream side operating chamber 42,43 under ejection path 105a, the situation of 106a in suction stroke, therefore, the refrigeration agent adverse current that can prevent to be ejected into downstream side operating chamber 42,43 from upstream side operating chamber 41,42 suction path 102e, the 103e of side operating chamber 42,43 downstream.
In addition, according to present embodiment, ejection path 105a, 106a owing to force down in upstream side operating chamber 41,42 under the situation of the interior pressure of downstream side operating chamber 42,43 seals, and the refrigeration agent that therefore can prevent downstream side operating chamber 42,43 is by ejection path 105a, 106a adverse current side operating chamber 41,42 upstream.
And, according to present embodiment, because ejection path 105a, 106a are formed at demarcation strip 105,106, and at one end portion is different with the other end for the aperture position (opening scope) of ejection path 105a, 106a, therefore, can utilize rotary plunger 31～33 to carry out the ejection path 150a that inscribes when complicated as described above, the switching of 106a.In other words, can constitute the mechanism of sealing ejection path 105a, 106a by rotary plunger 31～33.
Therefore, the situation that is specifically designed to mechanism's (for example valve system) of sealing ejection path 105a, 106a with setting is compared, and designs simplification can be made, and then number of spare parts can be cut down, and the reduction that realizes cost.
Especially, in the present embodiment, at one end portion is different with the other end for the aperture position (opening scope) that makes ejection path 105a, 106a, utilizes the 105b of through hole portion that the thickness direction with respect to demarcation strip 105,106 extends in parallel and the slot part 105c that extends along the plate face of demarcation strip 105,106 from the end of the 105b of through hole portion constitutes ejection path 105a.Therefore, for example, compare with the situation that is made of ejection path 105a, 106a the hole portion with respect to the thickness direction diagonally extending of demarcation strip 105,106, ejection path 105a, 106a can carry out easily with respect to the processing of demarcation strip 105,106.
In addition, according to present embodiment, because compressed refrigerant moves in three operating chamber, 41～43 associations, therefore the ejection of final refrigeration agent is carried out from the 3rd section operating chamber 43, does not carry out from the operating chamber 41,42 of first section and second section.Therefore, ejection valve (not shown) and each one of ejection chamber 24 are just enough.Therefore, each needs the technology of three (a plurality of) to compare with spray valve and ejection chamber for for example three separate compressed refrigerants of (a plurality of) operating chamber, and the reduction that can realize the reduction of number of spare parts and cost also has the miniaturization of build.
(second mode of execution)
In the above-described first embodiment, all ejection path 105a are made of 105b of through hole portion and slot part 105c, but in this second mode of execution, as shown in Figure 7, only be to be made of through hole portion and slot part near an ejection path 105a of blade 51, remaining three ejection path 105a only are made of through hole portion.
According to present embodiment,, can only constitute the ejection path 105a of a part by through hole portion by change the allocation position of ejection path 105a with respect to above-mentioned first mode of execution.Therefore, can spray the processing of path 105a easilier with respect to demarcation strip 105.
In the present embodiment, other features can be identical with the feature of first mode of execution.
(the 3rd mode of execution)
In the above-described first embodiment, though the volume of cross section circular space 21～23, be that the maximum volume of each operating chamber 41～43 is identical, but in this 3rd mode of execution, shown in Fig. 8 (a) and Fig. 8 (b), the volume of cross section circular space 21～23, be that the maximum volume of each operating chamber 41～43 is along with reducing gradually from first section to the 3rd section.Fig. 8 (b) is the D-D sectional view of Fig. 8 (a).
So,, press the characteristic optimization in can making, further reduce cogging by the volume of each operating chamber 41～43 of suitable setting.
In the present embodiment, other feature can be identical with the feature of first mode of execution.
(the 4th mode of execution)
In the above-described first embodiment, though the mutual phase difference equalization (120 °) of each operating chamber 41～43, in this 4th mode of execution, shown in Fig. 9 (a) and Fig. 9 (b), the non-equalization of phase difference that each operating chamber 41～43 is mutual.Fig. 9 (b) is the E-E sectional view of Fig. 9 (a).
So,, press the characteristic optimization in can making, further reduce cogging by the phase difference of each operating chamber 41～43 of suitable setting.
In addition, switching and above-mentioned first mode of execution of ejection path 105a, the 106a of present embodiment are same, can be undertaken by rotary plunger 31～33.In addition, preferably suitably change of the configuration of ejection path 105a, 106a corresponding to the setting of the phase difference of each operating chamber 41～43.
(the 5th mode of execution)
In the respective embodiments described above, illustration the present invention is applicable to the example of rotary plunger formula compressor, but in this 5th mode of execution, the present invention is applicable to yoke chip (yoke vane type) compressor.
Shown in Figure 10 (a) and (b), (c), the yoke chip compressor of present embodiment has: the shell (inner peripheral surface formation parts) 60 and the axle 61 that is inserted in the shell 60 that form two cylinders.Figure 10 (b) is the D-D sectional view of Figure 10 (a), and Figure 10 (c) is the E-E sectional view of Figure 10 (a).
In the example of Figure 10, shell 60 be with bolt (not shown) axially (left and right directions of Fig. 2 (a)) go up divided four and cut apart case member 601,602,603,604 and cut apart case member 602,603,604 two demarcation strips 605,606 each other and carry out fastening fixing and formation with being sandwiched in.Cutting apart case member 601～604 and demarcation strip 605,606 is formed by aluminium.
Cut apart to be disposed in the case member 601～604 at four and be formed with in the axial direction circular port 602a, the 603a that connects cutting apart of axial center side on the case member 602,603.Therefore, cut apart inner peripheral surface 602b, the 603b that case member 602,603 forms the cross section toroidal.
With respect to this, be formed with tabular surface 601a on the case member 601 axial one cutting apart of distolateral (Fig. 2 (a) left end side) being disposed at, tabular surface 601a obturation is cut apart the circular port 602a of case member 602.
Thus, cutting apart between case member 601～603 and the demarcation strip 605,606, series connection forms the space 71,72 of two cross section circles in the axial direction.In addition, in the present embodiment, the internal diameter size of two cross section circular spaces 71,72 and volume equate mutually.
Two cross section circular spaces 71,72 constitute the operating chamber 81,82 that sucks refrigeration agent and compression.Therefore, demarcation strip 605,606 plays the effect as the separating part of separating two operating chamber 81～82.
Be disposed at axially cutting apart on the case member 604 of another distolateral (the right-hand member side of Figure 10 (a)) among cutting apart case member 601～604 at four, be formed with recess 604a towards axial one distolateral (left end side of Figure 10 (a)) opening.
Therefore, cutting apart formation space 73 between case member 604 and the demarcation strip 606.It is the ejection chamber of the refrigeration agent after operating chamber 81,82 is compressed by cross section circular space 71,72 that this space 73 constitutes ejection.
Axle 61 runs through non-central and demarcation strip 605,606 of three cross section circular spaces 71,72.The both end sides position of axle 61 can be supported by shell 60 rotatably through bearing 62,63.
Be formed with the hole 601c that is used for an end (left part of Figure 10 (a)) of axle 61 is linked to a driving mechanism (not shown) on the case member 601 cutting apart.Internal configurations at hole 601c is useful on the lip seal 64 that prevents freezing medium leakage.
In this example, owing to use motor that vehicle driving uses as the axle driving mechanism, so the pulley (not shown) and the magnetic clutch (not shown) of transmission from the driving force of motor arranged in a distolateral binding of axle 61.Can also use electric motor as the axle driving mechanism.
Dispose the discoid rotor (rotary component) 91,92 that links with axle 61 respectively at two cross section circular spaces 71,72.
The outside dimension of rotor 91,92 is less than the internal diameter size of cross section circular space 71,72, and the central part of rotor 91,92 is linked to axle 11.The distance that the outside dimension of rotor 91,92 is configured among the inner peripheral surface with axle 11 center and cross section circular space 71,72 between axle 11 nearest positions (hereinafter referred to as near portion) is identical.Therefore, rotor 91,92 can be connected to rotating near portion and one side of cross section circular space 71,72 on one side.In the present embodiment, the boundary dimension of rotor 91,92 is identical mutually.
Between cross section circular space 71,72 and rotor 91,92, form the operating chamber 81,82 that sucks refrigeration agent and compress.Below, for convenience of explanation, axial one distolateral operating chamber 81 is called first section operating chamber, axial another distolateral operating chamber 82 is called second section operating chamber.
Outer circumferential face at rotor 91,92 is formed with recess 91a, the 92a that caves in towards the inboard of rotor 91,92. Recess 91a, 92a form the groove shape on the entire axial length of rotor 91,92.
Tabular blade (zoning parts) 93,94 (can haunt) slidably and be inserted in recess 91a, 92a.Dispose the spring (not shown) of blade 93,94 being pushed to cross section circular space 71,72 inner peripheral surfaces at recess 91a, 92a.
Under the thrust of spring (not shown), blade 93,94 haunts from the outer circumferential face of rotor 91,92 corresponding to the rotational position of rotor 91,92 and is connected to the inner peripheral surface of cross section circular space 71,72.Therefore, operating chamber 81,82 is divided into two spaces by blade 93,94.
Below, for convenience of description, with blade 93,94 be connected to cross section circular space 71,72 near portion the time the angle of swing of rotor 91,92 be defined as 0 ° (with reference to Figure 11 (a)).In the present embodiment, two rotors 91,92 are linked to axle 61 according to the mode of mutual rotatable phase difference equalization.That is, rotor 91,92 mutual rotatable phase differences are set at 360 °/2=180 °.
Shown in Figure 10 (b), (c), cutting apart the suction port 65 that is formed with the refrigeration agent (not compressed refrigerant) that suction flows out from vaporizer 4 on the case member 604.Shown in Figure 10 (b), be formed with the suction path 602d that the refrigeration agent that will suck from suction port is supplied to operating chamber 81 cutting apart case member 602.
Suck path 602d at inner peripheral surface 602b opening.In this example, represent with the angle of swing of rotor 91 if suck the allocation position of path 602d, then at about 10～30 ° position (with reference to Figure 11).
Shown in Figure 10 (c), also be formed with on the case member 603 and suck the same suction path 603d of path 602d cutting apart.The allocation position of suction path 603d and shape etc. are identical with suction path 602d.
Shown in Figure 10 (a) and (b), be formed with the adjacent operating chamber 81,82 of connection ejection path 605a each other at demarcation strip 605.In the present embodiment, be formed with three ejection path 605a.If the allocation position of three ejection path 605a represents with the angle of swing of rotor 91,92, then about 270 °, about 310 °, about 350 ° position (with reference to Figure 11).Ejection path 605a is made of the circular port of the table back of the body that runs through demarcation strip 605.
Ejection path 605a is opened and closed by rotor 91,92.Figure 11 is the explanatory drawing that the structure that is opened and closed ejection path 605a by rotor 91,92 is described, by per 30 ° angle of swing represent rotor 91,92 revolve turn around during action.
Figure 12 (a) is the F-F sectional view of Figure 11 (a), and illustrative is the state that is sprayed path 605a by rotor 91,92 sealings.Figure 12 (b) is the G-G sectional view of Figure 11 (i), and illustrative is the state of being opened ejection path 605a by rotor 91,92.
On rotor 91, be formed with and be used to make ejection path 605a to be communicated in the access 91b of first operating chamber 81.As shown in figure 12, access 91b is made of the groove on the end face that is formed at demarcation strip 605 sides among the rotor 91.Specifically, access 91b is by extending and the radial groove that arrives the outer circumferential face of rotor 91,92 constitutes from the end of blade 93 sides to radial outside among the circumferencial direction of rotor 91,92 is the circumferencial direction groove of circular-arc extension and circumferencial direction groove near the position of blade 93.The circumferencial direction groove has the length that can coincide with two adjacent among three ejection path 605a ejection path 605a simultaneously.
Equally, on rotor 92, identical and mode that overlap is formed with and is used to make ejection path 605a to be communicated in the access 92b of second operating chamber 82 according to the access 92b of shape and rotor 91.
In Figure 11, rotor 91,92 rotates to clockwise direction.Below for convenience of explanation, the sense of rotation with rotor 91,92 singly is called sense of rotation.In addition, the angle of swing of rotor 91 is called first section angle of swing, the angle of swing of rotor 92 is called second section angle of swing.
Be that as Figure 12 (a) illustration, ejection path 605a is closed under the situation of angle of swing=180 °～30 ° of 0 °～210 ° and second section in the angle of swing of first section shown in Figure 11 (a)～(h).That is, the two end part of ejection path 605a are stopped up by rotor 91,92.
On the other hand, under the situation of angle of swing=60 of angle of swing=240 of first section shown in Figure 11 (i)～(l) °～330 ° and second section °～150 °, as Figure 12 (b) illustration, ejection path 605a opens.That is, the two end part of ejection path 105a overlap with access 91b, the 92b of rotor 91,92, therefore spray path 605a and are communicated with first operating chamber 81, second operating chamber 82.
Be formed with the final ejection path (not shown) that is communicated with operating chamber 82 and ejection chamber 73 at the demarcation strip 606 shown in Figure 10 (a).Dispose the ejection valve (not shown) that opens and closes final ejection path at demarcation strip 606.In the example of Figure 10, adopt the needle spring plate valve as the ejection valve, dispose the stopper (retainer) 66 of the aperture of restriction ejection valve at demarcation strip 606.The refrigeration agent of ejection chamber 73 is sprayed to condenser 2 from the ejiction opening (not shown) that is formed at shell 60.
Below, the action of said structure is described.When 61 rotations of axle driving mechanism (not shown) live axle, rotor 91,92 rotations.By the rotation of rotor 91,92, carry out suction stroke and compression stroke repeatedly in each operating chamber 81,82.
At this, suction stroke is: operating chamber 81,82 and suction path 602d, 603d are in connected state, are inhaled into the stroke of operating chamber 81,82 from the not compressed refrigerant that sucks path 602d, 603d.Compression stroke is: operating chamber 81,82 and suction path 602d, 603d are in non-connected state, the stroke of compressed refrigerant in operating chamber 81,82.
As mentioned above, operating chamber 81,82 is divided into two spaces by blade 93,94.Suction stroke is carried out in a side space among these two spaces, carries out compression stroke in the opposing party space.
Based on Figure 11 it is specifically described.At this, only describe for first section operating chamber 81, also identical for second section operating chamber 82 elemental motion.
During in angle of swing ≠ 0 of first section shown in Figure 11 (b)～(l) °, in two spaces that operating chamber 81 forms, carry out suction stroke, in another space, promptly carry out compression stroke in the space that is positioned at sense of rotation side (dextrorotation veer side) with respect to blade 93 in the space that is positioned at sense of rotation opposition side (being rotated counterclockwise the direction side) with respect to blade 93.
One side's of operating chamber 81 space begins suction stroke when becoming connected state with suction path 602d.Then, when becoming non-connected state, path 602d when suction stroke finishes, begins compression stroke in a side's of operating chamber 81 space with sucking.
Compression stroke finishes during in angle of swing=0 of first section shown in Figure 11 (a) °.Promptly, when first section angle of swing=0 °, because blade 93 is pressed on the face identical with the outer circumferential face of rotor 91 near portion by the inner peripheral surface of cross section circular space 71,72, therefore carry out the volume vanishing in the space of compression stroke, thereby compression stroke finishes.
So, if be conceived to a space among two spaces of operating chamber 81, axle 61 revolve take two turns during, suction stroke and compression stroke are carried out a circulation.On the other hand, if be conceived to operating chamber 81 integral body, then suction stroke and compression stroke are carried out at two spatial parallelisms of operating chamber 81, therefore, axle 61 revolve turn around during, suction stroke and compression stroke are respectively carried out once.
As mentioned above, be that ejection path 605a opens under 240 °～330 ° the situation in the angle of swing of first section shown in Figure 11 (i)～(l).Thus, be ejected into second section adjacent operating chamber 82 first section operating chamber 81 refrigerant compressed by ejection path 605a.
As mentioned above, because in second section operating chamber 82, rotatable phase lags behind 180 ° with respect to first section operating chamber 81, and second section angle of swing when therefore spraying path 605a and opening is 60 °～150 °.
Therefore, the space in the compression stroke among two spaces of second section operating chamber 82 (being in the space in the compression after the suction stroke end) supply is by first section operating chamber 81 refrigerant compressed.The result is in second section operating chamber 82, and the compressed refrigerant after being compressed by first section operating chamber 81 is blended in from the not compressed refrigerant that sucks path 602d supply and is compressed.
Then, when the interior pressure of second section operating chamber 82 reaches authorized pressure when above, ejection valve (not shown) is opened, and therefore, is ejected into ejection chamber 73 by the refrigeration agent after 82 compressions of second section operating chamber.
At this, be that the angle of swing of first section operating chamber 81 is 0 °～150 ° under 180 °～330 ° the situation second section angle of swing.That is, at this moment, owing to compression stroke in first section operating chamber 81 finishes to become suction stroke, therefore the interior pressure of first section operating chamber 81 becomes and is lower than the interior pressure of second section operating chamber 82.
At this moment, shown in Figure 11 (a)～(f), because ejection path 605a is closed, the refrigeration agent that therefore prevents second section operating chamber 82 is by spraying path 605a adverse current to first section operating chamber 81.
Figure 13 (a) is the coordinate diagram of pressing the change of (the interior pressure in the space among two spaces of operating chamber in the compression stroke) in the chamber of representing in the above-mentioned action.The angle of swing of the transverse axis of Figure 13 (a) is represented first section angle of swing.The dotted line of Figure 13 (a) is a comparative example, and total capacity and the operating chamber identical with present embodiment of expression operating chamber only has the change of pressure in the chamber in the yoke chip compressor of (cylinder).
As mentioned above owing to be set with 180 ° phase difference each other in operating chamber 81,82, therefore each operating chamber 81,82 carry out compression stroke during respectively stagger 180 °.
Therefore, in angle of swing=0 °～180 °, only by first section operating chamber 81 compressed refrigerant; In angle of swing=180 °～360 °, by first section operating chamber 81 and second section operating chamber 82 compressed refrigerant; In angle of swing=360 °～540 °, only by second section operating chamber 82 compressed refrigerant.
, same only with comparative example by in angle of swing=0 of first section operating chamber 81 compressed refrigerant °～180 °, press liter in the chamber.
By among angle of swing=180 of first section operating chamber 81 and second section operating chamber 82 compressed refrigerant °～360 °, in angle of swing=180 °～210 °, ejection path 605a does not open yet, and first section operating chamber 81 and second section operating chamber 82 are by isolated.
Therefore, in first section operating chamber 81, rising with crimping in the same chamber of comparative example, on the other hand owing to only be that compressed refrigerant is not compressed second section operating chamber 82, thus second section operating chamber 82 in force down interior pressure in first section operating chamber 81.
Then, in angle of swing=210 °～360 °, ejection path 605a opens, and the interior pressure of the interior pressure of first section operating chamber 81 and second section operating chamber 82 becomes impartial, afterwards first section and second section operating chamber 81,82 in press liter.Therefore, compare with comparative example, the rising of pressing in the chamber slows down slowly.
In addition, after angle of swing=about 360 °, the rising of pressing in the chamber stops, and this is because press the cracking pressure (authorized pressure) that reaches ejection valve (not shown) in the chamber, sprays valve and opens.
From Figure 13 (a) as can be known, in the present embodiment,, therefore compare at the comparative example of 360 ° of cylinders finishing with compression stroke because compression stroke is finished at 540 ° (360 °+180 °),, can make the rising of pressing in the chamber slow.Therefore, compare, can reduce cogging significantly, and in the cogging frequency, can make once component (primary components) be principal component (primary coil) with comparative example.At this, it is one-period to produce component once that a so-called component of degree n n is meant with 360 ° of angle of swing (rotor turns around).
Be elaborated for its effect.Figure 13 (b) is the coordinate diagram by the change of operating chamber 81, the 82 above-mentioned action lumen capacity of expression (capacity in the space among two spaces of operating chamber in the compression stroke).Figure 13 (c) is the coordinate diagram by the change of shaft torque in the above-mentioned action of operating chamber 81,82 expressions.Figure 13 (d) is the coordinate diagram of expression synthetic shaft torque after synthetic with the shaft torque of each operating chamber 81,82 among Figure 13 (c).
At this, shaft torque is the required torque of live axle 61, with pressing element in the variation of chamber capacity and the chamber relation is arranged.Specifically, press in the variation of chamber capacity and chamber that shaft torque becomes big under the big situation.
Therefore, change characteristic according to the chamber capacity of each operating chamber 81,82 shown in pressure and Figure 13 (b) in the chamber shown in Figure 13 (a), can obtain the shaft torque of each operating chamber 81,82 shown in Figure 13 (c), and then, can obtain the synthetic shaft torque shown in Figure 13 (d) by synthesizing the shaft torque of each operating chamber 41～43 shown in Figure 13 (c).In addition, the dotted line of Figure 13 (c), (d) is represented above-mentioned comparative example, i.e. shaft torque in the yoke chip compressor of the total capacity of an operating chamber and cylinder identical with present embodiment.
In the present embodiment, shown in Figure 13 (c), because the change characteristic of the shaft torque in each operating chamber 81,82 is significantly different mutually, therefore shown in Figure 13 (d), the change of synthesizing shaft torque can be suppressed less, and in synthetic shaft torque, avoid the compression stroke of each operating chamber 81,82 to produce big peak value, the generation of main peak value can be suppressed be 360 ° of angle of swing only once.
Therefore, can take into account low torque and change and hang down contrary characteristic in the such prior art of variation frequency.And, by realizing the low torque change, can make the action of yoke chip compressor smooth and easy, can reduce vibration.In addition, by realizing low variation frequency, can suppress and resonance at the various subsidiary engines of engine compartment configuration etc.
In addition, according to present embodiment, sealing downstream side operating chamber 82 under the ejection situation of path 605a in suction stroke, therefore, the refrigeration agent adverse current that can prevent to be ejected into downstream side operating chamber 82 from upstream side operating chamber 81 is the suction path 603d of side operating chamber 82 downstream.
In addition, according to present embodiment, ejection path 605a owing to force down in upstream side operating chamber 81 under the situation of the interior pressure of downstream side operating chamber 82 seals, and the refrigeration agent that therefore can prevent downstream side operating chamber 82 is by ejection path 605a adverse current side operating chamber 81 upstream.
And, according to present embodiment, because ejection path 605a is formed on the demarcation strip 606, and on rotor 91,92, be formed with and be used to make ejection path 605a to be communicated in access 91b, the 92b of first operating chamber 81, second operating chamber 82, therefore, can utilize rotor 91,92 to carry out the switching of the ejection path 605a that inscribes when complicated as described above.In other words, can constitute the mechanism of sealing ejection path 605a by rotor 91,92.
Therefore, the situation that is specifically designed to mechanism's (for example valve system) of sealing ejection path 605a with setting is compared, and designs simplification can be made, and then number of spare parts can be cut down, and the reduction that realizes cost.
Especially, in the present embodiment, ejection path 605a is made of the simple circular port that runs through demarcation strip 606, upstream side access 91b and downstream side access 92b are made of the groove that forms on the end face of rotor 91,92, therefore can spray the processing of path 605a and two access 91b, 92b easily.
In addition, upstream side access 91b and downstream side access 92b owing to have can coincide with the length of two adjacent among three ejection path 605a ejection path 605a simultaneously, therefore, can be in angle of swing=210 °～360 ° gamut continues to open ejection path 605a.Therefore, can will stablize ejection to second section operating chamber 82 by the refrigeration agent after 81 compressions of first section operating chamber.
In addition, since upstream side access 91b be formed at blade 93 near, therefore, can make last (angle of swing: 360 °) that proceeds to the compression stroke of first section operating chamber 81 from first section operating chamber 81 to the ejection of the refrigeration agent of second section operating chamber 82 well.
In addition, according to present embodiment, because compressed refrigerant moves in two operating chamber 81,82 associations, therefore the ejection of final refrigeration agent is carried out from second section operating chamber 82, does not carry out from first section operating chamber 81.Therefore, ejection valve (not shown) and each one of ejection chamber 73 are just enough.Therefore, each needs the technology of two (a plurality of) to compare with spray valve and ejection chamber for for example two separate compressed refrigerants of (a plurality of) operating chamber, and the reduction that can realize the reduction of number of spare parts and cost also has the miniaturization of build.
(the 6th mode of execution)
In the above-described 5th embodiment, though the volume of cross section circular space 71,72, the maximum volume that is each operating chamber 81,82 is identical, but in this 6th mode of execution, as shown in figure 14, the volume of cross section circular space 71,72, i.e. the maximum volume of each operating chamber 81,82, second section first section of ratio is little.
So,, press the characteristic optimization in can making, further reduce cogging by the volume of each operating chamber 81,82 of suitable setting.
(the 7th mode of execution)
In the above-described 5th embodiment, though the mutual phase difference equalization (180 °) of each operating chamber 81,82, in this 7th mode of execution, as shown in figure 15, the non-equalization of phase difference that each operating chamber 81,82 is mutual.Figure 15 (b) is the I-I sectional view of Figure 15 (a).
So,, press the characteristic optimization in can making, further reduce cogging by the phase difference of each operating chamber 81,82 of suitable setting.
In addition, switching and above-mentioned first mode of execution of the ejection path 605a of present embodiment are same, can be undertaken by rotor 91,92.In addition, preferably suitably change of the configuration of ejection path 605a corresponding to the setting of the phase difference of each operating chamber 81,82.
(other mode of executions)
In addition, the respective embodiments described above are expression ejection path 105a, the configuration of 106a, 605a and an example of shape only, can also carry out various distortion to configuration and the shape of ejection path 105a, 106a, 605a.
In addition, in the respective embodiments described above, though open and close ejection path 105a, 106a, 605a by rotary plunger 31～33 or rotor 91,92, can also open and close ejection path 105a, 106a, 605a with valve system (for example needle spring plate valve or solenoid valve etc.).
For example, the ejection path can be formed at shell, open and close the ejection path with valve system.In addition, the ejection path can also be formed at blade, open and close the ejection path by haunting of blade.In addition, the ejection path can also be formed at axle, the rotation by axle opens and closes the ejection path.
In addition, in the respective embodiments described above, though form inner peripheral surface 101b, 102b, 103b, 602b, 603b by shell 10,60, can also accommodate cylinder block (cylinder block) at shell, on cylinder block, form inner peripheral surface 101b, 102b, 103b, 602b, 603b.
In addition, in above-mentioned first～the 4th mode of execution,, be not limited thereto, the present invention can also be applicable to have two rotary plunger formula compressors with upper cylinder though show the example that the present invention is applicable to the rotary plunger formula compressor of three cylinders.
In addition, in above-mentioned the 5th～the 7th mode of execution,, be not limited thereto, the present invention can also be applicable to have three yoke chip compressors with upper cylinder though show the example that the present invention is applicable to the yoke chip compressor of two cylinders.
In addition, the present invention is applicable to various rotary compressors such as bosh blade (bosh vane) formula compressors.At this, so-called bosh vane compressor is meant: be connected to the inner peripheral surface of cross section elliptical shape in the rotor and rotate, the compressor that blade haunts from the outer circumferential face of rotor.In addition, in the bosh vane compressor, the sectional shape of inner peripheral surface can not be the elliptical shape on the tight meaning, can be roughly elliptoid special side-glance shape.
In addition, in the respective embodiments described above, show the present invention is applicable to the example of compression vehicle with the compressor of the refrigeration agent of refrigeration cycle, but be not limited thereto, the present invention can also be widely used in compressing the compressor of various fluids.

Claims (11)

1. a compressor is characterized in that,
It possesses many group inner peripheral surfaces and forms parts (10,60), rotary component (31,32,91,92) and divide parts (51,52,93,94), described inner peripheral surface forms parts (10,60) form the inner peripheral surface (101b that stipulates shape, 102b, 602b, 603b), described rotary component (31,32,91,92) with described inner peripheral surface (101b, 102b, 602b, 603b) join and rotate, described division parts (51,52,93,94) at described inner peripheral surface (101b, 102b, 602b, 603b) with described rotary component (31,32,91,92) space that forms between is divided
In described inner peripheral surface forms parts (10,60) between each described inner peripheral surface (101b, 102b, 602b, 603b) and described rotary component (31,32,91,92) and the described division parts (51,52,93,94), formation sucks the suction stroke of fluid and the operating chamber (41,42,81,82) of compression stroke that the described fluid that is sucked by described suction stroke is compressed
Rotary component (31,91) among a plurality of described rotary components (31,32,91,92) is more forward than the rotatable phase of other described rotary component (32,92),
The operating chamber (41,81) that is formed by a described rotary component (31,91) among with a plurality of described operating chamber (41,42,81,82) is during as the upstream side operating chamber, form at described inner peripheral surface and to be formed with ejection path (105a, 605a) on the parts (10,60), other operating chamber (42,82) described ejection path (105a, 605a) compresses described fluid after described suction stroke is finished among described upstream side operating chamber (41,81) is formed into a plurality of described operating chamber (41,42,81,82).
2. compressor as claimed in claim 1 is characterized in that,
Possess when with described other operating chamber (42,82) during, in described upstream side operating chamber (41,81), force down the mechanism (31,32,91,92) of the described ejection path of sealing (105a, 605a) under the situation of the interior pressure of described downstream side operating chamber (42,82) as the downstream side operating chamber.
3. compressor as claimed in claim 2 is characterized in that,
Described upstream side operating chamber (41,81) and described downstream side operating chamber (42,82) axially go up disposed adjacent described upstream side operating chamber (41,81),
Described inner peripheral surface forms parts (10,60) and has the tabular separating part (105,605) of separating described upstream side operating chamber (41,81) and described downstream side operating chamber (42,82),
Described ejection path (105a, 605a) is formed at described separating part (105,605),
The mechanism that seals described ejection path (105a, 605a) is made of described rotary component (31,32,91,92).
4. as each described compressor in the claim 1～3, it is characterized in that,
The cross section of described inner peripheral surface (101b, 102b) is circular,
Described rotary component (31,32) is the discoid rotary plunger along the eccentric rotation of described inner peripheral surface (101b, 102b),
Described division parts (51,52) are to haunt from described inner peripheral surface (101b, 102b) and be connected to the blade of described rotary plunger (31,32).
5. compressor as claimed in claim 3 is characterized in that,
The cross section of described inner peripheral surface (101b, 102b) is circular,
Described rotary component (31,32) is the discoid rotary plunger along the eccentric rotation of described inner peripheral surface (101b, 102b),
Described division parts (51,52) are to haunt from described inner peripheral surface (101b, 102b) and be connected to the blade of described rotary plunger (31,32),
Described upstream side operating chamber (41) and described downstream side operating chamber (42) axially go up disposed adjacent described upstream side operating chamber (41),
Described inner peripheral surface forms parts (10) and has the tabular separating part (105) of separating described upstream side operating chamber (41) and described downstream side operating chamber (42),
Described ejection path (105a) is formed at described separating part (105),
The end of the end of described upstream side operating chamber (41) side and described downstream side operating chamber (42) side among described ejection path (105a) is with respect to the opening scope difference of described separating part (105).
6. compressor as claimed in claim 5 is characterized in that,
The slot part (105c) that extends along the plate face of described separating part (105) from the end of described upstream side operating chamber (41) among through hole portion (105b) that described ejection path (105a) is extended in parallel by the thickness direction with respect to described separating part (105) and the described through hole portion (105b) constitutes.
7. as each described compressor in the claim 1～3, it is characterized in that,
The cross section of described inner peripheral surface (602b, 603b) is circular,
Described rotary component (91,92) is connected to described inner peripheral surface (602b, 603b) and rotor rotated in being,
Described division parts (93,94) are that the outer circumferential face from described rotor (91,92) haunts and is connected to the blade of described inner peripheral surface (602b, 603b).
8. compressor as claimed in claim 3 is characterized in that,
The cross section of described inner peripheral surface (602b, 603b) is circular,
Described rotary component (91,92) is connected to described inner peripheral surface (602b, 603b) and rotor rotated in being,
Described division parts (93,94) are that the outer circumferential face from described rotor (91,92) haunts and is connected to the blade of described inner peripheral surface (602b, 603b),
Described upstream side operating chamber (81) and described downstream side operating chamber (82) axially go up disposed adjacent described upstream side operating chamber (81),
Described inner peripheral surface forms parts (60) and has the tabular separating part (605) of separating described upstream side operating chamber (81) and described downstream side operating chamber (82),
Described ejection path (605a) is formed at described separating part (605),
The end of described upstream side operating chamber (81) side overlaps with the described rotor (91) that forms described upstream side operating chamber (81) among the described ejection path (605a),
The end of described downstream side operating chamber (82) side overlaps with the described rotor (92) that forms described downstream side operating chamber (82) among the described ejection path (605a),
On the described rotor (91) that forms described upstream side operating chamber (81), be formed with the upstream side access (91b) that described ejection path (605a) is communicated with described upstream side operating chamber (81),
On the described rotor (92) that forms described downstream side operating chamber (82), be formed with the downstream side access (92b) that described ejection path (605a) is communicated with described downstream side operating chamber (82).
9. compressor as claimed in claim 8 is characterized in that,
Described upstream side access (91b) is made of the groove that forms at the end face of described separating part (605) side among the described rotor (91) that forms described upstream side operating chamber (81),
Described downstream side access (92b) is made of the groove that forms at the end face of described separating part (605) side among the described rotor (92) that forms described downstream side operating chamber (82).
10. as each described compressor in the claim 1～3, it is characterized in that,
With described other operating chamber (42,82) during as the downstream side operating chamber,
The maximum volume of described downstream side operating chamber (42,82) is less than the maximum volume of described upstream side operating chamber (41,81).
11. as each described compressor in the claim 1～3, it is characterized in that,
The described rotary component (31,32,91,92) that forms a plurality of operating chamber (41,42,81,82) is constituted as the mutual non-equalization of rotatable phase difference.
CN2010105225431A 2009-11-04 2010-10-26 Compressor Pending CN102052318A (en)

Applications Claiming Priority (4)

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JP2009253023 2009-11-04
JP2009-253023 2009-11-04
JP2010089512A JP5273085B2 (en) 2009-11-04 2010-04-08 Compressor
JP2010-089512 2010-04-08

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CN104121193A (en) * 2014-07-24 2014-10-29 珠海凌达压缩机有限公司 Rotary compressor
CN106704191A (en) * 2017-03-07 2017-05-24 东莞市风能工业设备有限公司 Multi-stage cam compressor

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CN101169116A (en) * 2007-11-17 2008-04-30 美的集团有限公司 Exhaust valve device of rotary compressor and control method thereof
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JPH01277695A (en) * 1988-04-28 1989-11-08 Toshiba Corp Two-cylinder type rotary compressor
CN1239757A (en) * 1998-06-22 1999-12-29 三星电子株式会社 Rotary compressor having plurality of compression chambers for multistage compression
CN1264792A (en) * 2000-03-17 2000-08-30 李辛沫 Blade-type rotary compressor
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Application publication date: 20110511