CN101397998B - Slide holding device of rotary compressor and control method thereof - Google Patents
Slide holding device of rotary compressor and control method thereof Download PDFInfo
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- CN101397998B CN101397998B CN2008102188946A CN200810218894A CN101397998B CN 101397998 B CN101397998 B CN 101397998B CN 2008102188946 A CN2008102188946 A CN 2008102188946A CN 200810218894 A CN200810218894 A CN 200810218894A CN 101397998 B CN101397998 B CN 101397998B
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Abstract
The invention relates to relates to a sliding vane holding device of a rotary compressor and a controlling method thereof; a motor and a compressing component connected with the motor are arranged in a sealed shell in which the pressure is a high-pressure side; the compressing component comprises two cylinders, and an intermediate baffle is arranged between the cylinders; each cylinder are held in a cylinder cavity of a circular piston which can carry out a free eccentric rotation; the sliding of a sliding vane is set in a sliding vane groove; the rear end part of the sliding vane is held in a sliding vane cavity; the sliding vane is pressed, and the front end of the sliding vane is in contact with and closely follows with the outer diameter of the circular piston, wherein, a first sliding cavity is provided with a spring connected with the sliding vane. The sliding vane holding device is characterized in that a cross hole is arranged on a second cylinder; one end of the cross hole is at the high-pressure side, and the other end of the cross hole is at the sliding groove of the second cylinder; a first concave part with a diameter more than the diameter of the cross hole is arranged on the lateral motion surface of a second sliding vane corresponding to the cross hole; a second sliding vane cavity is communicated with one end of a pressure switching pipe, and the other end of the pressure switching pipe stretches out of the shell and is communicated with a pressure switching valve.
Description
Technical field
The present invention relates to the slide holding device and the controlling method thereof of a kind of rotary compressor, particularly a kind of rotary compressor.
Background technique
In recent years, along with twin-tub rotation-type compressor is applied on the air conditioner,, end the compression of cylinder, thereby the method for control compressor refrigerating capacity is open as an example wherein.Representation example as these cold control techniques, the internal pressure in airtight slide plate chamber, perhaps the pressure of cylinder compression chamber switches between low pressure and high-pressure, pass through holding device, make slide plate away from piston direction, keep slide plate in inside, slide plate chamber, and remove that to keep ending, remove the method for ending the cylinder chamber compression open.As Japan Patent: patent is opened and is put down into the 1-247786 communique, it is patent documentation 1, with patent disclosure 2004-301114 communique, be that the disclosed design problem that occurs when making slide plate away from piston is in the patent documentation 2: be difficult in the slide plate chamber of little volume be equipped with such as large-scale plants such as magnet or extension springs, and the moment of cylinder chamber compression termination, and remove the moment of ending, the problem of unstable vibrations will take place in slide plate; Particularly the instability vibrations of slide plate can bring following integrity problem: slide plate front end and piston periphery bump against the problems such as slide plate damage that the slide plate that causes is beated sound and produced therefrom.
Summary of the invention
Purpose of the present invention aims to provide a kind of simple and reasonable, slide plate long service life, slide plate front end and piston periphery not to be had to bump against and produces the beat slide holding device of rotary compressor of sound of slide plate, to overcome deficiency of the prior art.
Press the slide holding device of a kind of rotary compressor of this purpose design, the housing internal pressure is in the on high-tension side seal casinghousing, the compression assembly of taking in motor and being connected with this motor, compression assembly comprises two cylinders, first cylinder and second cylinder, be provided with central diaphragm between the cylinder, each cylinder is taken in the cylinder chamber of the circular piston that carries out free eccentric rotary, slide plate is slidingly arranged in the vane slot, end, the slide plate back side is taken in the slide plate chamber, slide plate is subjected to the pushing effect, its front end contacts with the external diameter of described circular piston and closely follows, and wherein is provided with the spring that joins with slide plate in first slide plate chamber, it is characterized in that second cylinder is provided with cross-drilled hole, this cross-drilled hole one end perforate is in the high pressure side, the other end perforate is in the vane slot of second cylinder, and to being provided with first recess of diameter greater than the aperture of cross-drilled hole by cross-drilled hole, the second slide plate chamber is switched Guan Yiduan with pressure and is communicated with on the first side moving surface of second slide plate, the other end that pressure switches pipe stretches out outside the housing, communicates with the pressure switching valve.
The second side moving surface to the side of the first side moving surface of described second slide plate is provided with second recess, and the bypass groove that is opened on the second slide plate chamber is communicated with second recess.
Described cross-drilled hole passes the vane slot of second cylinder, form pressure hole and low pressure hole respectively, be slidingly arranged on the side moving surface of second slide plate in the vane slot of second cylinder, corresponding respectively pressure hole and low pressure hole are provided with first recess and second recess, and the diameter of first recess and second recess is all greater than the aperture of cross-drilled hole.
Described central diaphragm is provided with the gas channel that leads to first cylinder chamber and second cylinder chamber respectively, and this gas channel communicates with air aspiration cavity in being arranged on second cylinder, and air aspiration cavity communicates with second cylinder chamber, and the low pressure hole communicates with air aspiration cavity.
Described side moving surface is upper and lower both sides or and arranged on left and right sides, and cross-drilled hole one end perforate is in oil sump.
Gap between the described second slide plate front end and the second piston periphery is less than or equal to 10 μ m.
A kind of controlling method of slide holding device of rotary compressor, it is characterized in that high-pressure is imported in first recess of the first side moving surface in two side moving surfaces that are arranged at second slide plate at least, press to the active force of vane slot inner face with the first side moving surface that produces second slide plate, and make the opposition side of the first side moving surface of second slide plate, just produce frictional force between the second side moving surface and second vane slot, thereby second slide plate is stopped and remaining on conscientiously in the second slide plate chamber.
Low pressure is imported in second recess of second side moving surface of opposition side of first side moving surface of second slide plate.
The bypass groove of the second side moving surface of the opposition side of the first side moving surface by being arranged on second slide plate is communicated to the second slide plate chamber, makes its pressure between the two equate that wherein, the bypass groove communicates with second recess.
Described high-pressure is produced by pressurized gas or high pressure oil.
The invention provides a kind of beat method of mail topic of slide plate that in the rotary compressor of control slide plate action, control refrigerating capacity, solves, when compressor operation, always on the side moving surface of slide plate one side, apply high-pressure, apply low pressure on the side moving surface of relative therewith slide plate opposite side, make slide plate press to vane slot by this pressure reduction; And be provided at the technological scheme that also can increase this pressure under the prerequisite of not sacrificing compressor performance.
By pressure hole and the low pressure hole of perforate in each side moving surface of second slide plate, make the side moving surface of slide plate produce side pressure, consequently: when sheet stopped to move, the gap that forms between the periphery of second piston of the front end of slide plate and idle running was very little, so second slide plate moment is static.And, to remove when static, the slide plate front end can contact with the periphery of second piston moment, and this technological scheme can prevent the sound of beating of slide plate.Can effectively improve the static and confining force of slide plate by first recess on the side moving surface that is arranged on slide plate and second recess.When the compression of cylinder chamber is ended, be minimum on the gap principle that produces between slide plate front end and the piston.Thereby the slide plate front end the slide plate seismism can not occur during away from piston, and also can not produce the slide plate vibrations should remove away from effect the time.And, the slide plate front end can moment away from piston, can remove moment again away from effect, its result can prevent that the beat generation and the slide plate of sound of slide plate is impaired, thereby prolongs the working life of slide plate.
Description of drawings
Fig. 1 is the vertical section structure schematic representation of first embodiment of the invention.
Fig. 2 is that the A-A ' of Fig. 1 is to the broken section structural representation.
Fig. 3-Fig. 4 is the not amplification perspective view of ipsilateral of two of second slide plates.
Cross-sectional structure schematic representation when Fig. 5 is in compression for first embodiment of the invention.
Cross-sectional structure schematic representation when Fig. 6 stops to compress for first embodiment of the invention is in.
Fig. 7 is the second embodiment of the invention structural representation.
Fig. 8-Fig. 9 is the amplification perspective view of another structure of second slide plate in the third embodiment of the invention.
Figure 10 is the cross-sectional structure schematic representation of third embodiment of the invention.
Figure 11 is the vertical section structure schematic representation of fourth embodiment of the invention.
Among the figure: 1 is rotary compressor, and 2 is housing, and 3 is compression assembly, and 4 is motor, 5a is first cylinder, and 5b is second cylinder, and 6 is central diaphragm, and 7a is first cylinder chamber, 7b is second cylinder chamber, and 11 is screw, and 12 is main bearing, 13 is supplementary bearing, and 14 is three-way diverter valve, and 15 is vane slot, 16a is a vane slot H face, and 16b is a vane slot L face, and 17 is gas channel, 18 is air aspiration cavity, and 21a is first slide plate, and 21b is second slide plate, 22a is a first piston, and 22b is second piston, and 23a is first sucking pipe, 23b is second sucking pipe, and 24a is the first slide plate chamber, and 24b is the second slide plate chamber, 25 is coil spring, and 26 is bent axle, and 31 is high-voltage tube, 33 is cross-drilled hole, and 34 is pressure hole, and 35 is the low pressure hole, 36 is oil sump, and 37 is the bypass groove, and 41 are pressure switching pipe, 42a is first recess, and 42b is second recess, and 43 is liquid-storage container.
Embodiment
Below in conjunction with drawings and Examples the present invention is further described.
First embodiment
Referring to Fig. 1, be the internal structure of rotary compressor 1 of the present invention.The interior pressure of seal casinghousing 2 is the high pressure side, and the bottom is provided with compression assembly 3, and top is provided with motor 4, and their outer diameter part is fixed in the internal diameter of housing 2.Compression assembly 3 has the first cylinder 5a and two cylinders of the second cylinder 5b, separates with central diaphragm 6 between two cylinders, forms the first cylinder chamber 7a and the second cylinder 7b respectively.Wherein, the discharge capacity of the second cylinder 5b is less than the discharge capacity of the first cylinder 5a, and the method that realizes this design is the height dimension that changes arbitrary cylinder.
On the first cylinder 5a and the second cylinder 5b below with screw 11 main bearing 12 and supplementary bearing 13 are installed respectively, in the first cylinder chamber 7a and the second cylinder chamber 7b of sealing, the first piston 22a and the second piston 22b are installed on the eccentric part of bent axle 26, can free off-centre rotate, and be accommodated in the first cylinder chamber 7a and the second cylinder chamber 7b.
The first slide plate 21a and the second slide plate 21b are inserted into 15 li of the vane slots of the first cylinder 5a and the second cylinder 5b, and the first slide plate chamber 24a and the second slide plate chamber 24b are formed at the back of slide plate.The front end of the first slide plate 21a inserted coil spring 25 among the first slide plate chamber 24a, so can always be pressed to the external diameter of first piston 22a.
The upper and lower opening portion of the second slide plate chamber 24b is isolated from the pressure of on high-tension side housing 2 by central diaphragm 6 and supplementary bearing 13 sealings.The second slide plate chamber 24b switches pipe 41 1 ends with pressure and is communicated with, the other end that pressure switches pipe 41 stretches out outside the housing 2, be communicated with three-way diverter valve (not having diagram), play the effect that imports pressure, the internal pressure of the second slide plate chamber 24b can be switched between high pressure side and low voltage side.
The first sucking pipe 23a that is opened on the first cylinder chamber 7a is installed in the first cylinder 5a, and the other end of first sucking pipe is communicated with liquid-storage container 43.The cold media air of low pressure flows to the first sucking pipe 23a from liquid-storage container 43, when the gas after first cylinder 5a shunting is drawn among the first cylinder chamber 7a, as shown in Figure 2, flow to the air aspiration cavity 18 that is arranged in the second cylinder 5b through the gas channel 17 that is arranged on the central diaphragm 6, be drawn into again among the second cylinder chamber 7b.
Referring to Fig. 2, the vane slot 15 in each cylinder has two inner faces, promptly has vane slot H face 16a and vane slot L face 16b.
The first slide plate 21a and the second slide plate 21b are inserted in the vane slot respectively, and follow above-mentioned two face slide relative of vane slot.Cross-drilled hole 33 from the outside perforate always of the second cylinder 5b in the passage-air aspiration cavity 18 that sucks gas, after the second slide plate 21b installs, cross-drilled hole 33 is divided into pressure hole 34 and low pressure hole 35 by the second slide plate 21b, pressure hole 34 perforates are in vane slot H face 16a, and 35 perforates of low pressure hole are in vane slot L face 16b.And the aperture portion perforate of cross-drilled hole 33 is seen Fig. 1 in oil sump 36.
Each side moving surface of the second slide plate 21b is respectively equipped with the first recess 42a and the second recess 42b as shown in Figure 3 and Figure 4.The first recess 42a and the second recess 42b are communicated with pressure hole 34 and low pressure hole 35 respectively when the second slide plate 21b is still in the vane slot.The shape of this recess is not only circular, and can be rectangular, and ellipse waits other shape, its number can for one and more than, its degree of depth can be very shallow, 0.05mm is just enough to 0.1mm.
The following describes the effect of above-mentioned twin-tub rotation-type compressor.As the pressure with internal diameter is the low pressure hole 35 of on high-tension side pressure hole 34 relative perforates, and its pressure is low voltage side, and as shown in Figure 2, the side of the second slide plate 21b produces directed force F.So the second slide plate 21b will be pressed on the vane slot L face 16b of low pressure hole 35 perforates.This directed force F multiply by the value of the friction factor that produces between the side of the second slide plate 21b and the vane slot L face 16b, and the static force of ending slide plate reciprocating action exactly, this power also become the slide plate confining force after static.But second cylinder chamber 7b when running slide plate is being done reciprocating action, so with respect to the reciprocating action of slide plate, above-mentioned static force has played the effect of viscous force.
Directed force F is the variate-value that product determined of the pressure reduction that produces between the area of the first recess 42a and the second recess 42b and pressure hole 34 and the low pressure hole 35.
Promptly be equivalent to: F ∝ η * (P
Pressure hole* S
First recess-P
The low pressure hole* S
Second recess),
Wherein, η is a friction factor, P
Pressure holeBe the pressure of pressure hole, S
First recessBe the area of the first recess 42a, P
The low pressure holeBe the pressure in low pressure hole, S
Second recessIt is the area of the second recess 42b.
If above-mentioned friction factor is the definite value of material, surface roughness and lubricating status decision, strengthen the area of the first recess 42a and the second recess 42b so, confining force will increase; Reduce this area, confining force will descend.Same, strengthen the area difference of the first recess 42a and the second recess 42b, confining force will increase, and reduce this area difference, and confining force will descend.
When compressor operation, always can produce above-mentioned slide plate static force.When the second slide plate chamber 24b when switching the high pressure side, act on the second slide plate 21b back, to make slide plate press to the pushing force of the second piston 22b periphery more much bigger than slide plate static force, so the second slide plate 21b can not stop the continuation compression.Fig. 5 has shown this state.
When the second slide plate chamber 24b switched to low voltage side, the back pressure of the second slide plate 21b became with the pressure of the second cylinder chamber 7b and equates, or less than the pressure of the second cylinder chamber 7b, so the counterpressure at the second slide plate 21b back is zero.At this in a flash, slide plate is still in top dead center, and promptly to be projected into the overhang of cylinder chamber be zero position to the slide plate front end, and remain on the vane slot L face 16b.Therefore, second piston 22b idle running, compression is ended.Fig. 6 has shown this state.
When the second slide plate chamber 24b switched to the high pressure side once more, the second slide plate 21b was projected among the second cylinder chamber 7b once more, and with the periphery moment contact of the second piston 22b, the second cylinder chamber 7b just can carry out compression.Just return to the state of Fig. 5.
At this moment, the front end of the second slide plate 21b is stopped on the interior radial line of cylinder compression chamber 7b, and the gap between general and the second piston 22b periphery that dallies is below the 10 μ m feature of the present invention that Here it is.And even the compressor long-term operation causes slide plate front end or piston periphery to produce abrasion, changing still can not appear in its gap each other.
Inertial force when slide plate reciprocating action is mainly followed in this gap is relevant with the directed force F of slide plate, and directed force F is big more, and the viscous force that acts on slide plate reciprocating action is just big more, and this gap is just more little.
Because the slide plate quality is little, perhaps slide plate speed waits slowly and cause inertial force than hour, can reduce directed force F.Under such condition, the second recess 42b or the some of the second recess 42a that are configured on the slide plate can omit so; When the actuating pressure that uses refrigerant was high, the second recess 42b and two of the second recess 42a can omit.
In the disclosed in the past technology, have pressure slide plate is pulled to retaining mechanism away from piston direction, because the gap between control slide plate front end and idle running piston periphery is difficult to, so have to strengthen the gap.To this, the gas pressure of the side moving surface of the present invention by acting on slide plate, the viscous force of utilizing the frictional force action that produces between slide plate and the vane slot to produce in slide plate reciprocating action is zero top dead center in slide plate speed, can make slide plate static and remain in vane slot or the slide plate chamber.Therefore, the present invention has and above-mentioned slide plate front end can be become minimum feature with the gap design that dallies between the piston periphery.Consequently: both can stop the reciprocating action of slide plate moment, also can the abrupt release slide plate, and, because the gap is very little, so slide plate front end contact piston periphery can not produce impulsive sound.
In order to increase directed force F, also can enlarge the aperture in pressure hole 34 and low pressure hole 35, but, this method can be brought problem: the resistance force diminishes of the gas of the pressure hole of flowing through or oil, when the second slide plate chamber 24b switches to low voltage side, when ending compression, can reduce the efficient of compressor to high pressure oil or gas in the second slide plate chamber 24b from the clearance leakage that produces between the second slide plate 21b and the vane slot 15, and the problem that causes oil to release; When the second slide plate chamber 24b switches to the high pressure side, when continuing compression, the high pressure air of the second slide plate chamber 24b is known from experience through low pressure hole 35 and is flowed out to air aspiration cavity 18, may cause the decrease in efficiency of compressor.
The present invention optimizes the size of the next free control action power F of area of the first recess 42a and the second recess 42b by dwindle the aperture in pressure hole 34 and low pressure hole 35 as far as possible, and the appearance that its result can avoid above-mentioned topic to ask is accomplished to prevent trouble before it happens.Because directed force F is followed in the cylinder compression chamber, the side pressure of the side moving surface that acts on slide plate that gas compression brings by comparison, and is much smaller far away, and point of action is near the center of slide plate, so can not have influence on the abrasion of the side moving surface of slide plate.
Conclusion among first embodiment is to act on the side moving surface of slide plate by directed force F to obtain, and when active force F acts on the side moving surface of upper and lower side of slide plate, also can obtain and effect and effect that first embodiment is identical substantially.
Second embodiment
Referring to Fig. 7, present embodiment is a design proposal of having omitted the low pressure hole 35 of using among first embodiment.When the second slide plate chamber 24b switches to low voltage side, termination compression, in two gaps between the second slide plate 21b and the vane slot 15: the gap of vane slot H face 16a is the high pressure side because of the effect of the first recess 42a certainly, the gap of vane slot L face 16b also is a part low pressure even without low pressure hole 35, thereby produces directed force F.Therefore, the design proposal of some rotary compressor can adopt second embodiment.
The 3rd embodiment
Referring to Fig. 8 and Fig. 9, designed the second recess 42b in the present embodiment, to replace low pressure hole 35 illustrated among first embodiment.In the side of the second slide plate 21b, the bypass groove 37 that is opened on the second slide plate chamber 24b is communicated with the second recess 42b.
When the second slide plate chamber 24b switches to the high pressure side, when the second cylinder chamber 7b continued compression, the bypass groove 37 and the second recess 42b were all the high pressure side.Because the pressure hole 34 and the first recess 42a also are the high pressure sides, so the directed force F of slide plate side is almost nil.
When the second slide plate chamber 24b switched to low voltage side, the bypass groove 37 and the second recess 42b were all low voltage side, so produce and the almost equal directed force F of first embodiment.So the second slide plate 21b is static and remain on the vane slot L face 16b.Figure 10 has shown this state.
Compare with first embodiment, in the 3rd embodiment, directed force F is very little during the slide plate action, so the slippage loss of slide plate can not increase.But when slide plate was static, bypass groove 37 was a part low pressure, can bring into play with first embodiment to equate, or be higher than first embodiment's slide plate static force and confining force.
Therefore, the present invention has following feature: by importing pressurized gas or the high pressure oil side to the side moving surface of slide plate, import low-pressure gas to the side moving surface of the slide plate of opposition side, so that produce frictional force between the side moving surface of the low voltage side of slide plate and the vane slot, thereby slide plate is stopped and remaining on conscientiously in the slide plate chamber.
The 4th embodiment
Referring to Figure 11, shown in patent documentation 2 like that, used embodiments of the invention switching to by pressure in the twin-tub rotation-type compressor that on high-tension side method stops slide plate action, control refrigerating capacity with cylinder chamber.
The second cylinder 5b that constitutes compression assembly 3 connects the end of the second sucking pipe 23b, its the other end reaches the outside of housing 2, be connected on the attachment tube of three-way diverter valve 14, two attachment tubes of all the other of three-way diverter valve 14 are connected in the high-voltage tube 31 and liquid-storage container 43 that is soldered on the housing 2.The end of the first sucking pipe 23a is connected with the first cylinder 5a, and its other end is directly connected on the liquid-storage container 43.Because the upper and lower aperture portion of the second slide plate chamber 24b of the second cylinder 5b opens in the housing 2, so high pressure side always.But as first embodiment was said, the second cylinder 5b was furnished with the second slide plate 21b, pressure hole 34 and low pressure hole 35, and the first recess 42a and the second recess 42b are arranged on the slide plate, so can produce with the identical directed force F of first embodiment.When the second sucking pipe 23b was communicated with liquid-storage container 43 by three-way diverter valve 14, the second cylinder 5b continued common compression.
But, by three-way diverter valve 14, with the second sucking pipe 23b switch to the same high pressure side of housing 2 after, the pressure of the second cylinder chamber 7b becomes the high pressure side, with the equilibrium of forces that acts on the second slide plate 21b back.Make the second slide plate 21b static and remain in the second slide plate chamber 24b at this momentary action power F.Consequently second piston 22b idle running, compression stops.When switching three-way selector valve 14 once more, inject low-pressure gas for the second sucking pipe 23b after, the ridge of high pressure pressure that acts on the second slide plate 21b back can be removed the state of rest of slide plate, the second cylinder 5b restarts compression.
As mentioned above, the present invention can simple application in as disclosed in the patent documentation 1, switch in the two-cylinder type compressor that on high-tension side method stops slide plate action, control refrigerating capacity by pressure cylinder chamber.What disclosed technological scheme was passable among the present invention simply imports in the industry, and drops into and produce in batches, and its possibility that is used on the industry is also very big.
Claims (10)
1. the slide holding device of a rotary compressor (1), the housing internal pressure is on high-tension side seal casinghousing (2) lining, the compression assembly (3) of taking in motor (4) and being connected with this motor, compression assembly comprises two cylinders, first cylinder (5a) and second cylinder (5b), be provided with central diaphragm (6) between the cylinder, each cylinder is taken in the cylinder chamber of the circular piston that carries out free eccentric rotary, slide plate is slidingly arranged in the vane slot, end, the slide plate back side is taken in the slide plate chamber, slide plate is subjected to the pushing effect, its front end contacts with the external diameter of described circular piston and closely follows, wherein be provided with the spring that joins with slide plate in first slide plate chamber, it is characterized in that second cylinder is provided with cross-drilled hole (33), this cross-drilled hole one end perforate is in the high pressure side, the other end perforate is in the vane slot (15) of second cylinder, on the first side moving surface of second slide plate (21b) to being provided with first recess (42a) of diameter by cross-drilled hole greater than the aperture of cross-drilled hole, the second slide plate chamber (24b) is switched pipe (41) one ends with pressure and is communicated with, the other end that pressure switches pipe stretches out outside the housing, communicates with the pressure switching valve.
2. according to the slide holding device of the described rotary compressor of claim 1, the second side moving surface to the side that it is characterized in that the first side moving surface of described second slide plate (21b) is provided with second recess (42b), and the bypass groove (37) that is opened on the second slide plate chamber (24b) is communicated with second recess.
3. according to the slide holding device of the described rotary compressor of claim 1, it is characterized in that described cross-drilled hole (33) passes the vane slot (15) of second cylinder, form pressure hole (34) and low pressure hole (35) respectively, be slidingly arranged on the side moving surface of second slide plate (21b) in the vane slot of second cylinder, corresponding respectively pressure hole and low pressure hole are provided with first recess (42a) and second recess (42b), and the diameter of first recess and second recess is all greater than the aperture of cross-drilled hole.
4. according to the slide holding device of the described rotary compressor of claim 3, it is characterized in that described central diaphragm (6) is provided with the gas channel (17) that leads to first cylinder chamber (7a) and second cylinder chamber (7b) respectively, this gas channel communicates with the air aspiration cavity (18) that is arranged on second cylinder (5b) lining, air aspiration cavity communicates with second cylinder chamber, and low pressure hole (35) communicate with air aspiration cavity.
5. according to the slide holding device of the described rotary compressor of the arbitrary claim of claim 1 to 3, it is characterized in that described side moving surface is upper and lower both sides or and arranged on left and right sides, cross-drilled hole (33) one end perforates are in oil sump (36).
6. according to the slide holding device of the described rotary compressor of claim 1, it is characterized in that the gap between described second slide plate (21b) front end and second piston (22b) periphery is less than or equal to 10 μ m.
7. controlling method of the slide holding device of rotary compressor according to claim 1, it is characterized in that high-pressure is imported in first recess of the first side moving surface in two side moving surfaces that are arranged at second slide plate at least, press to the active force of vane slot inner face with the first side moving surface that produces second slide plate, and make the opposition side of the first side moving surface of second slide plate, just produce frictional force between the second side moving surface and second vane slot, thereby second slide plate is stopped and remaining on conscientiously in the second slide plate chamber.
8. according to the controlling method of the slide holding device of the described rotary compressor of claim 7 (1), it is characterized in that low pressure is imported in second recess of second side moving surface of opposition side of first side moving surface of second slide plate.
9. according to the controlling method of the slide holding device of the described rotary compressor of claim 7 (1), the bypass groove of second side moving surface that it is characterized in that the opposition side of the first side moving surface by being arranged on second slide plate, be communicated to the second slide plate chamber, its pressure is between the two equated, wherein, the bypass groove communicates with second recess.
10. according to the controlling method of the slide holding device of the described rotary compressor of claim 7 (1), it is characterized in that described high-pressure is produced by pressurized gas or high pressure oil.
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| CN2008102188946A CN101397998B (en) | 2008-10-31 | 2008-10-31 | Slide holding device of rotary compressor and control method thereof |
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| CN2008102188946A CN101397998B (en) | 2008-10-31 | 2008-10-31 | Slide holding device of rotary compressor and control method thereof |
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| CN101397998A CN101397998A (en) | 2009-04-01 |
| CN101397998B true CN101397998B (en) | 2011-05-25 |
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| CN102562594B (en) * | 2010-12-30 | 2014-07-23 | 广东美芝制冷设备有限公司 | Capacity-varying rotary type compressor |
| CN103321907B (en) * | 2012-03-22 | 2016-07-06 | 广东美芝制冷设备有限公司 | Rotary compressor |
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| WO2017061014A1 (en) * | 2015-10-08 | 2017-04-13 | 三菱電機株式会社 | Rotary compressor |
| CN105508248A (en) * | 2016-01-19 | 2016-04-20 | 广东美芝制冷设备有限公司 | Capacity-variable compressor |
| CN109185141A (en) * | 2018-10-25 | 2019-01-11 | 珠海凌达压缩机有限公司 | For the compression mechanism of compressor, compressor and air conditioner |
| CN114060272B (en) * | 2021-12-08 | 2023-02-24 | 珠海格力电器股份有限公司 | Compression structure, compressor and air conditioner with same |
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2008
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