CN202203117U - Double-cylinder rotary compressor - Google Patents

Double-cylinder rotary compressor Download PDF

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Publication number
CN202203117U
CN202203117U CN2011202797072U CN201120279707U CN202203117U CN 202203117 U CN202203117 U CN 202203117U CN 2011202797072 U CN2011202797072 U CN 2011202797072U CN 201120279707 U CN201120279707 U CN 201120279707U CN 202203117 U CN202203117 U CN 202203117U
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China
Prior art keywords
cylinder
piston
compression chamber
pressure
internal diameter
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Expired - Lifetime
Application number
CN2011202797072U
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Chinese (zh)
Inventor
小津政雄
黄水松
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Anhui Meizhi Precision Manufacturing Co Ltd
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Anhui Meizhi Precision Manufacturing Co Ltd
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Priority to CN2011202797072U priority Critical patent/CN202203117U/en
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Abstract

The utility model relates to a double-cylinder rotary compressor. A sealed shell is provided with a compressor mechanism and a motor; the compressor mechanism comprises a first cylinder with a first compression cavity, a second cylinder with a second compression cavity, and a middle clapboard; the first cylinder is internally provided with a first piston and a first slip sheet; the second cylinder is internally provided with a second piston and a second slip sheet; an eccentric crankshaft drives the first piston and the second piston simultaneously and comprises a first eccentric shaft and a second eccentric shaft; a main bearing and a sub-bearing for supporting the eccentric crankshaft in a slipping way are respectively arranged on the side surfaces of the first cylinder and the second cylinder; compared with the displacement of the first cylinder, the displacement of the second cylinder is less; and compared with the inner diameter of the first compression cavity of the first cylinder, the inner diameter of the second compression cavity of the second cylinder is smaller. A second slip sheet cavity on the second cylinder is connected with a pressure switching pipe, and the pressure of the pressure switching pipe is switched between suction pressure and discharge pressure of the first cylinder. The double-cylinder rotary compressor provided by the utility model has the characteristics of good safety performance and wide application range.

Description

Twin-tub rotation-type compressor
Technical field
The utility model relates to a kind of twin-tub rotation-type compressor, specifically is loss in efficiency and the reliability problems that solves the twin-tub rotation-type compressor that is applied to air-conditioning and freezing machine.
Background technique
Two twin-tub rotation-type compressors that cylinder is formed by different displacements; The more variable volume controlled rotary compressor of refrigerating capacity that is used for; Wherein, the height dimension of the cylinder that discharge capacity is less diminishes, rigidity reduces, and the less cylinder of this discharge capacity not only the precision reduction can occur in the processing of component and assembly process; And under the effect of the inside and outside differential pressure of compression chamber, also can produce distortion, therefore can cause the problems such as slippage loss and abrasion problem of piston.
[patent documentation 1] Japanese Patent Laid is opened the 2008-128231 volume variable rotating compressor.
[patent documentation 2] Chinese patent document number CN1761817A rotary closed type compressor and refrigerating circulatory device.
The model utility content
The purpose of the utility model aims to provide a kind of simple and reasonable, flexible operation, twin-tub rotation-type compressor that Safety performance is good, applied widely, to overcome deficiency of the prior art.
A kind of twin-tub rotation-type compressor by this purpose design; The housing of sealing is provided with compressing mechanism and motor; Compressing mechanism comprises first cylinder that has first compression chamber, second cylinder and the central diaphragm that has second compression chamber; Be provided with the first piston and first slide plate in first cylinder, be provided with second piston and second slide plate in second cylinder, eccentric crankshaft drives the first piston and second piston simultaneously; Eccentric crankshaft comprises first eccentric shaft and second eccentric shaft; Be used for the main bearing of sliding support eccentric crankshaft and the side that supplementary bearing is separately positioned on first cylinder and second cylinder, its structure characteristic is the discharge capacity with respect to first cylinder, and the discharge capacity of second cylinder is less; With respect to the internal diameter of first compression chamber of first cylinder, the internal diameter of second compression chamber of second cylinder is less.
The second slide plate chamber on said second cylinder and pressure switch pipe and join, and the pressure that pressure switches pipe switches between the suction pressure of first cylinder and head pressure.
With respect to the external diameter of first eccentric shaft, the external diameter of second eccentric shaft reduces.
With respect to the internal diameter of main bearing, the internal diameter of supplementary bearing reduces.
The internal diameter of second cylinder of the utility model through will be less with respect to first displacement volume reduces; Consequently; Second cylinder not only height dimension increases, and the minimum wall thickness (MINI W.) in the second slide plate chamber also increases, and finally causes second cylinder can increase substantially rigidity; Therefore, can prevent to have the loss in efficiency and the integrity problem of the twin-tub rotation-type compressor of float amount cylinder in advance.
The utility model not only can be applicable to twin-tub rotation-type compressor, and is applicable to the twin-tub rotation-type compressor of volume controlled, and it has simple and reasonable, flexible operation, good, the advantage of wide range of application of Safety performance.
Description of drawings
Fig. 1 is the embodiment's 1 of the utility model a structural representation.
Fig. 2 is the structure for amplifying schematic representation of the compressing mechanism among the embodiment 1.
Fig. 3 is the dimensioned drawing of the compressing mechanism among the embodiment 1.
Fig. 4 is the main TV structure schematic representation of first cylinder among the embodiment 1.
Fig. 5 is the broken section structural representation of first cylinder among the embodiment 1.
Fig. 6 is the main TV structure schematic representation of second cylinder among the embodiment 1.
Fig. 7 is the broken section structural representation of second cylinder among the embodiment 1.
Fig. 8 is the main TV structure schematic representation of first cylinder in the twin-tub rotation-type compressor in the past.
Fig. 9 is the broken section structural representation of first cylinder in the twin-tub rotation-type compressor in the past.
Figure 10 is the main TV structure schematic representation of second cylinder in the twin-tub rotation-type compressor in the past.
Figure 11 is the broken section structural representation of second cylinder in the twin-tub rotation-type compressor in the past.
Figure 12 is the embodiment's 2 of the utility model a structural representation.
Among the figure: R is a rotary compressor, and 2 is housing, and 4 is compressing mechanism, and 5 is motor, and 6 is sucking pipe, and 13a is first cylinder; 13b is second cylinder, and 14a is first compression chamber, and 14b is second compression chamber, and 15 is the cylinder screw, and 17a is a first piston, and 17b is second piston; 18a is first slide plate, and 18b is second slide plate, and 19a is the first slide plate chamber, and 19b is the second slide plate chamber, and 20 for pressure switches pipe, and 21 is eccentric crankshaft; 21a is a main shaft, and 21b is a countershaft, and 22a is first eccentric shaft, and 22b is second eccentric shaft, and 25 is main bearing, and 26 is supplementary bearing; 31 is first exhaust port, and 32 is second exhaust port, and 35 is the bottom baffler, and 40 is central diaphragm, and 41 is center hole.
Embodiment
Below in conjunction with accompanying drawing and embodiment the utility model is further described.
Embodiment 1
The utility model is the cylinder designing technique with twin-tub rotation-type compressor of difference cylinder discharge capacity, and is special relevant with volume controlled rotary compressor.In the twin-tub rotation-type compressor that possesses the volume controlled technology, like [patent documentation 1] and [patent documentation 2],, stop the gas compression in the cylinder compression chamber through making the piston idle running of a cylinder, control refrigerating capacity.In above-mentioned document, the discharge capacity of two cylinders equates, so can between 100% and 50%, carry out volume controlled.
For the air-conditioning that is used for refrigeration and heats, require heating capacity to improve 1.2~1.4 times scope than refrigerating capacity.Based on this demand, the refrigerating capacity that for example when two cylinder operation, heats is in 100%, and the refrigerating capacity of refrigeration is 80% during the single cylinder running.At this moment, heat with the ability ratio that freezes and become 1.25 times.
In such design, if the internal diameter of the compression chamber of two cylinders is identical, the height ratio of the height of first cylinder and second cylinder is 4: 1, and for example: when the height of first cylinder was 28mm, the height of second cylinder was 7mm.The main target of the utility model is to prevent the too hour generation distortion of cylinder cylinder height.
Referring to twin-tub rotation-type compressor R shown in Figure 1, include motor 5 and compressing mechanism 4 in the housing 2 of sealing.Compressing mechanism 4 is made up of the first cylinder 13a and two cylinders of the second cylinder 13b, the central diaphragm 40 of separating them, eccentric crankshaft 21, main bearing 25 and supplementary bearing 26 etc.These compression key element parts connect through cylinder screw 15.After compressing mechanism 4 assemblings were accomplished, the periphery of main bearing 25 was fixed on the inwall of housing 2.
Referring to Fig. 2 and Fig. 3, shown the details of compressing mechanism 4.In the first compression chamber 14a and the second compression chamber 14b that the central authorities of the first cylinder 13a and the second cylinder 13b constitute; Dispose the first piston 17a and the second piston 17b of eccentric operating, and contact the also first slide plate 18a and the second slide plate 18b of reciprocating operation with these pistons.The first slide plate chamber 19a that will constitute at these slide plate backs in addition,, the second slide plate chamber 19b and separately the minimum wall thickness (MINI W.) between the outer wall of cylinder be expressed as Va and Vb respectively.
The eccentric crankshaft 21 that drives two pistons simultaneously has through main bearing 25 and supplementary bearing 26 and carries out the main shaft 21a and the countershaft 21b of sliding support, the first eccentric shaft 22a that makes above-mentioned two piston eccentric operating and the second eccentric shaft 22b.Main bearing 25 is provided with first exhaust port 31 that the pressurized gas in the first compression chamber 14a are discharged, and is same, and supplementary bearing 26 is provided with second exhaust port 32 that the pressurized gas in the second compression chamber 14b are discharged.More than compression key element parts assemble through cylinder screw 15, are assembled into compressing mechanism 4.
Referring to Fig. 3, first compression chamber 14a compression is the low-pressure gas of Ps from the pressure that sucking pipe 6 sucks, and the gas after overcompression is discharged to the inside of housing 2 from first exhaust port 31.Second compression chamber 14b compression is from the low-pressure gas of sucking pipe 6 shuntings, through the gas after the overcompression from second exhaust port 32 via the bottom baffler 35 that is arranged on the supplementary bearing 26, be discharged to the inside of housing 2.
Relevant twin-tub rotation-type compressor, the cylinder design concept of the utility model is seen Fig. 3 and Fig. 4-Fig. 7.Fig. 3 representes is that the internal diameter of the first compression chamber 14a and the second compression chamber 14b is respectively Da and Db, and the cylinder height of the first compression chamber 14a and the second compression chamber 14b is respectively Ha and Hb.The first cylinder 13a is different with the internal diameter of the second compression chamber 14b with the inner columniform first compression chamber 14a that constitutes of the second cylinder 13b, the inside diameter D b of the inside diameter D a of the first compression chamber 14a>second compression chamber 14b.
Discharge capacity can be calculated through (the external diameter area of the internal diameter area-piston of compression chamber) * cylinder height as estimate.That is to say square being directly proportional of the internal diameter of discharge capacity and compression chamber.Therefore, when discharge capacity one timing, if the inside diameter D of compression chamber diminishes, the height of cylinder can increase greatly; If it is big that the internal diameter of compression chamber becomes, the height of cylinder can reduce greatly.
In rotary compressor, when the profile of cylinder is identical conditions, generally acknowledge that the size to the tool influence of cylinder rigidity is the minimum wall thickness (MINI W.) V in slide plate chamber, the height H of cylinder and the internal diameter of compression chamber.In addition, the length L of vane slot must be certain above size, so big if the internal diameter of compression chamber becomes, the minimum wall thickness (MINI W.) in slide plate chamber can diminish.
In Fig. 4-Fig. 7, the first cylinder 13a is with respect to the second cylinder 13b, and the cylinder height of the first cylinder 13a is higher, and the discharge capacity of the first cylinder 13a is bigger, and is therefore bigger to the compression efficiency influence that brings because of the cylinder design.Therefore, at first, the inside diameter D a of the first compression chamber 14a and the dimensional ratios of cylinder height H a are optimized from the viewpoint of compression efficiency.
Because the discharge capacity of the first cylinder 13a is bigger, so can not sacrifice the rigidity of cylinder, realizes the optimization of Da/Ha simply.That is to say that the inside diameter D a of the compression chamber of the first cylinder 13a and cylinder height H a can guarantee enough big size.Therefore, like Fig. 4-shown in Figure 7,, also can guarantee the rigidity of the first cylinder 13a even the minimum wall thickness (MINI W.) Va of the first slide plate chamber 19a is smaller.
But, because the discharge capacity of the second cylinder 13b is less than normal significantly, so make design optimization from the viewpoint of guaranteeing the cylinder rigidity.That is to say, in the inside diameter D b of the compression chamber that reduces the second cylinder 13b, the minimum wall thickness (MINI W.) Vb in the second slide plate chamber and the cylinder height H b of the second compression chamber 14b are increased.As a result,, can increase Vb and height H b, guarantee the rigidity of the second cylinder 13b like Fig. 4-shown in Figure 7.
Referring to Fig. 8-Fig. 9, be cases of design in the past.The compression chamber internal diameter of second cylinder and first cylinder all is identical dimension D a, and is the same with the inside diameter D a of the compression chamber of first cylinder among the embodiment 1.Therefore; Embodiment 1 second cylinder 13b and the second routine in the past cylinder are compared; Embodiment 1 is no matter be minimum wall thickness (MINI W.) Vb, or any of the internal diameter of the cylinder height H b of the second compression chamber 14b or the second compression chamber 14b in the second slide plate chamber; It is natural having superiority, and the rigidity of second cylinder among the embodiment 1 also especially has superiority with respect to the rigidity of in the past second cylinder.
As stated, the technology that discloses among the embodiment 1, low through the rigidity that prevents second cylinder less with respect to first displacement volume, not only in component processing and assembly process, second vane slot that takes place in also avoiding turning round and the distortion of second compression chamber.Can obtain and prevent to produce the reliability of twin-tub rotation-type compressor and the effect of inefficiency problem in advance.
In addition, in embodiment 1, because with respect to the first compression chamber 14a, the internal diameter of the second compression chamber 14b reduces, so with respect to first piston 17a, be necessary to reduce external diameter and the piston inner diameter of the second piston 17b.Therefore, with respect to the external diameter of the first eccentric shaft 22a, be necessary to reduce the external diameter of the second eccentric shaft 22b.In addition,, be necessary to reduce external diameter Sd and the internal diameter of supplementary bearing 26 of the countershaft 21b of eccentric crankshaft 21, more be necessary to reduce the internal diameter of intermediate hole 41 with respect to the external diameter Ld of the main shaft 21a of eccentric crankshaft 21.
Whether for the understanding of top this section words be: consequently, can avoid the gas at the pressure between Ps~Pd of the periphery of the second piston 17b that makes eccentric operating, the pressure that enter in the center hole 41 are in the scope of Pd.Even the internal diameter of center hole 41 more also can be assemblied in central diaphragm 40 between first eccentric shaft and second eccentric shaft than the second piston 17b internal diameter.
Embodiment 2
Referring to Fig. 6, present embodiment is the example that embodiment 1 announcement technology is applied to the twin-tub rotation-type compressor of volume controlled.The same with embodiment 1, with respect to the first cylinder 13a, the discharge capacity of the second cylinder 13b reduces significantly.
Embodiment 2 volume controlled mode; For example shown in [patent documentation 1]; Pressure through being connected with the second slide plate chamber 19b switches pipe 20; The pressure of the second slide plate chamber 19b is switched between the suction pressure Ps of the first cylinder 13a and head pressure Pd, make second slide plate 18b to-and-fro motion or the stop motion.
When the second slide plate 18b is static, second piston 17b idle running, the second compression chamber 14b is generally low voltage side Ps.Between the outer wall of the second compression chamber 14b and the second cylinder 13b, produce very big pressure difference.Make the second compression chamber 14b receive load from the outer wall of the second cylinder 13b.
But because embodiment 1 the second cylinder 13b has enough rigidity, so the second compression chamber 14b is indeformable, the second piston 17b of eccentric operating can continue the idle running of safety.In addition, [patent documentation 2] such occasion that the volume controlled mode is different equally also can obtain above-mentioned effect.

Claims (5)

1. twin-tub rotation-type compressor; The housing (2) of sealing is provided with compressing mechanism (4) and motor (5); Compressing mechanism (4) comprises first cylinder (13a) that has first compression chamber (14a), second cylinder (13b) and the central diaphragm that has second compression chamber (14b); Be provided with first piston (17a) and first slide plate (18a) in first cylinder (13a); Be provided with second piston (17b) and second slide plate (18b) in second cylinder (13b); Eccentric crankshaft (21) drives first piston (17a) and second piston (17b) simultaneously, and eccentric crankshaft (21) comprises first eccentric shaft (22a) and second eccentric shaft (22b), is used for the main bearing (25) of sliding support eccentric crankshaft (21) and the side that supplementary bearing (26) is separately positioned on first cylinder (13a) and second cylinder (13b); It is characterized in that the discharge capacity with respect to first cylinder (13a), the discharge capacity of second cylinder (13b) is less; With respect to the internal diameter of first compression chamber (14a) of first cylinder (13a), the internal diameter of second compression chamber (14b) of second cylinder (13b) is less.
2. twin-tub rotation-type compressor according to claim 1; It is characterized in that the second slide plate chamber (19b) and pressure on said second cylinder (13b) switches pipe (20) and joins, the pressure that pressure switches pipe (20) switches between the suction pressure of first cylinder (13a) and head pressure.
3. twin-tub rotation-type compressor according to claim 1 and 2 is characterized in that the external diameter with respect to first eccentric shaft (22a), and the external diameter of second eccentric shaft (22b) reduces.
4. twin-tub rotation-type compressor according to claim 3 is characterized in that the internal diameter with respect to main bearing (25), and the internal diameter of supplementary bearing (26) reduces.
5. twin-tub rotation-type compressor according to claim 1 is characterized in that the internal diameter with respect to main bearing (25), and the internal diameter of supplementary bearing (26) reduces.
CN2011202797072U 2011-08-03 2011-08-03 Double-cylinder rotary compressor Expired - Lifetime CN202203117U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2011202797072U CN202203117U (en) 2011-08-03 2011-08-03 Double-cylinder rotary compressor

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Application Number Priority Date Filing Date Title
CN2011202797072U CN202203117U (en) 2011-08-03 2011-08-03 Double-cylinder rotary compressor

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114320A (en) * 2015-08-18 2015-12-02 广东美芝制冷设备有限公司 Rotary volume-variable enhanced vapor injection compressor
CN106762643A (en) * 2016-12-05 2017-05-31 珠海格力节能环保制冷技术研究中心有限公司 Cylinder, pump assembly and compressor
WO2018103476A1 (en) * 2016-12-05 2018-06-14 珠海格力节能环保制冷技术研究中心有限公司 Air cylinder, pump body assembly, compressor, and temperature adjusting apparatus
CN111255688A (en) * 2018-11-30 2020-06-09 上海海立电器有限公司 Air conditioning system and variable frequency compressor thereof

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114320A (en) * 2015-08-18 2015-12-02 广东美芝制冷设备有限公司 Rotary volume-variable enhanced vapor injection compressor
CN106762643A (en) * 2016-12-05 2017-05-31 珠海格力节能环保制冷技术研究中心有限公司 Cylinder, pump assembly and compressor
WO2018103476A1 (en) * 2016-12-05 2018-06-14 珠海格力节能环保制冷技术研究中心有限公司 Air cylinder, pump body assembly, compressor, and temperature adjusting apparatus
US11105331B2 (en) 2016-12-05 2021-08-31 Green Refrigeration Equipment Engineering Research Center of Zhuhai Gree Co., Ltd Cylinder, pump body assembly, compressor, and temperature adjusting device
CN111255688A (en) * 2018-11-30 2020-06-09 上海海立电器有限公司 Air conditioning system and variable frequency compressor thereof

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Granted publication date: 20120425

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