CN105114312A - Double-cylinder rotating compressor - Google Patents
Double-cylinder rotating compressor Download PDFInfo
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- CN105114312A CN105114312A CN201510599155.6A CN201510599155A CN105114312A CN 105114312 A CN105114312 A CN 105114312A CN 201510599155 A CN201510599155 A CN 201510599155A CN 105114312 A CN105114312 A CN 105114312A
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Abstract
The invention discloses a double-cylinder rotating compressor which comprises a first air cylinder, a second air cylinder, a middle partition plate located between the first air cylinder and the second air cylinder, and a crankshaft. The crankshaft comprises a first core deflecting shaft, a second core deflecting, a main shaft and an auxiliary shaft, wherein the first core deflecting shaft and the second core deflecting shaft drive a first rolling piston and a second rolling piston respectively, and the main shaft and the auxiliary shaft are in sliding supporting with a main bearing and an auxiliary bearing which are connected with the first air cylinder and the second air cylinder respectively. At least one of the first core deflecting shaft and the second core deflecting shaft is in sliding fit or pressing fit with the crankshaft, and a torque transmission part is arranged between the corresponding core deflecting shaft and the crankshaft. According to the double-cylinder rotating compressor in the embodiment, the core deflecting amount of the crankshaft can be improved, the design degrees of freedom of a compression cavity, the rolling pistons, a sliding piece and the like are expanded, and the design for improving the compression efficiency can be conducted.
Description
Technical field
The present invention relates to compressor field, especially relate to a kind of twin-tub rotation-type compressor.
Background technique
Within about 1988, formally batch twin-tub rotation-type compressor produced is with single cylinder rotary compressor compared with, and the interior on a large scale vibration operated from low speed to high speed, noise aspect are all outstanding.Further, be reply large scale system in recent years, advance the application expanding 10HP to.On the other hand, in the assembling of twin-tub rotation-type compressor, in the center hole of the central diaphragm of segmentation 2 compression chambers, the torque-transmitting axle of bent axle is through.Thus, the center bore that there is central diaphragm must be more than or equal to the problem of torque-transmitting axle external diameter.
Due to this problem, relative to single cylinder rotary compressor, the bent axle core shift amount of twin-tub rotation-type compressor can not strengthen.Its result, due to compression chamber, the design size of rolling piston and slide plate etc. is limited, and can not carry out the optimal design of compression efficiency.
In order to the path of above-mentioned center hole, find out in correlation technique and central diaphragm is divided into the method for 2 parts and used.But, highly difficult manufacturing technology is needed for the gap of central diaphragm and the control of planeness.
Summary of the invention
The present invention is intended to solve one of technical problem in correlation technique at least to a certain extent.For this reason, the present invention proposes a kind of twin-tub rotation-type compressor, can increase the core shift amount of bent axle.
According to the twin-tub rotation-type compressor of the embodiment of the present invention, comprising: the 1st cylinder and the 2nd cylinder, described 1st cylinder has the 1st compression chamber, and described 2nd cylinder has the 2nd compression chamber; Central diaphragm between described 1st cylinder and described 2nd cylinder; The 1st rolling piston and the 2nd rolling piston of eccentric rotary is carried out respectively in described 1st compression chamber and described 2nd compression chamber; The 1st slide plate slided with described 1st rolling piston and described 2nd rolling piston synchronous reciprocating respectively and the 2nd slide plate; Bent axle, described bent axle comprise drive the 1st torque-transmitting axle of described 1st rolling piston and described 2nd rolling piston and the 2nd torque-transmitting axle respectively, the main shaft of the main bearing that is connected respectively with described 1st cylinder and described 2nd cylinder and supplementary bearing sliding support and countershaft; At least one of described 1st torque-transmitting axle and described 2nd torque-transmitting axle is slidably matched with described bent axle or is pressed into cooperation, possesses transmission of torque part between which.
According to the twin-tub rotation-type compressor of the embodiment of the present invention, be slidably matched by least one making the 1st torque-transmitting axle and the 2nd torque-transmitting axle with bent axle or be pressed into and coordinate, therefore the core shift amount of bent axle can be increased, the design freedom of compression chamber, rolling piston and slide plate etc. expands, and can carry out the design improving compression efficiency.
Particularly, described transmission of torque part is key or moment rod.
In some embodiments of the invention, described 1st torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, and the central diaphragm internal diameter of described central diaphragm is greater than the external diameter of described main shaft and is less than the external diameter of described 1st torque-transmitting axle; And/or described 2nd torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, the central diaphragm internal diameter of described central diaphragm is greater than the external diameter of described countershaft and is less than the external diameter of described 2nd torque-transmitting axle.
In some embodiments of the invention, the external diameter of described countershaft is less than the external diameter of described main shaft.
In some embodiments of the invention, described central diaphragm is the thrust slip surface supporting described bent axle load.
In some embodiments of the invention, described 1st torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, and the axial action amplitude of described 1st torque-transmitting axle is limited by described central diaphragm and described main bearing; And/or described 2nd torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, the axial action amplitude of described 2nd torque-transmitting axle is limited by described central diaphragm and described supplementary bearing.
In some embodiments of the invention, and described 1st torque-transmitting axle that coordinates of described bent axle and/or described 2nd torque-transmitting axle be sintered alloy part or be forged into shaped piece.
Accompanying drawing explanation
Fig. 1 and embodiments of the invention 1 are correlated with, and are the internal structure longitudinal section of twin-tub rotation-type compressor;
Fig. 2 is correlated with embodiment 1, is the longitudinal section of compression mechanical part;
Fig. 3 is correlated with embodiment 1, is the planimetric map of central diaphragm;
Fig. 4 is correlated with embodiment 1, is the comparison diagram that in the past designed relevant with bent axle core shift amount with the configuration rolling piston in compression chamber;
Fig. 5 is correlated with embodiment 1, is the details drawing of bent axle;
Fig. 6 is correlated with case study on implementation 1, is the details drawing (90 degree of rotations) of bent axle;
Fig. 7 is correlated with case study on implementation 1, is the sectional view of torque-transmitting axle and the External view of key;
Fig. 8 and embodiments of the invention 2 are correlated with, and are the longitudinal sections of compression mechanical part;
Fig. 9 and embodiments of the invention 3 are correlated with, and are the details drawings of bent axle;
Figure 10 is correlated with case study on implementation 3, is the sectional view of torque-transmitting axle and the External view of moment rod;
Figure 11 is correlated with embodiments of the invention 4, is the longitudinal section of compression mechanical part.
Reference character:
Twin-tub rotation-type compressor 1, housing 2,
Motor 4, rotor 4a,
Compression mechanical part 5, central diaphragm 40, central diaphragm internal diameter 40a, the 1st cylinder 11, the 2nd cylinder 21, main bearing 43, supplementary bearing 45, the 1st compression chamber 11a, the 2nd compression chamber 21a, the 1st rolling piston 51, the 2nd rolling piston 52, the 1st slide plate 53, the 2nd slide plate 54, the 1st baffler 43a, the 2nd baffler 45a, key 36, circular groove 46,
Bent axle 30, the 1st torque-transmitting axle 34, the 2nd torque-transmitting axle 35, main shaft 31, countershaft 33, jack shaft 32, keyway 33a (35e), the 1st thrust top 34a, the 1st thrust bottom 34b, the 2nd thrust 35a, oil groove 35c, oilhole 35d, axle center hole 30a, moment rod 38, moment rod groove 38b, moment rod hole 33b,
1st sucking pipe 55, the 2nd sucking pipe 56, liquid-storage container 60.
Embodiment
Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.
In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", " counterclockwise ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise at least one this feature.In describing the invention, the implication of " multiple " is at least two, such as two, three etc., unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection or each other can communication; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements, unless otherwise clear and definite restriction.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.
The twin-tub rotation-type compressor 1 according to the embodiment of the present invention is described in detail below with reference to Fig. 1-Figure 11.
According to the twin-tub rotation-type compressor 1 of the embodiment of the present invention, comprising: the 1st cylinder 11, the 2nd cylinder 21, the central diaphragm 40 between the 1st cylinder 11 and the 2nd cylinder 21, the 1st rolling piston 51, the 2nd rolling piston 52, the 1st slide plate 53, the 2nd slide plate 54, bent axle 30.1st cylinder 11 has the 1st compression chamber 11a, and the 2nd cylinder 21 has the 2nd compression chamber 21a.1st rolling piston 51 and the 2nd rolling piston 52 carry out eccentric rotary respectively in the 1st compression chamber 11a and the 2nd compression chamber 21a.
1st slide plate 53 and the 2nd slide plate 54 slide with the 1st rolling piston 51 and the 2nd rolling piston 52 synchronous reciprocating respectively.
Bent axle 30 comprise drive the 1st torque-transmitting axle 34 of the 1st rolling piston 51 and the 2nd rolling piston 52 and the 2nd torque-transmitting axle 35 respectively, the main shaft 31 of the main bearing 43 that is connected respectively with the 1st cylinder 11 and the 2nd cylinder 21 and supplementary bearing 45 sliding support and countershaft 33.
At least one of 1st torque-transmitting axle 34 and the 2nd torque-transmitting axle 35 is slidably matched with bent axle 30; Or at least one of the 1st torque-transmitting axle 34 and the 2nd torque-transmitting axle 35 is pressed into bent axle 30 and coordinates, and possesses transmission of torque part between which.
That is, twin-tub rotation-type compressor 1 comprises: the 1st cylinder 11, the 2nd cylinder 21, central diaphragm 40, the 1st rolling piston 51, the 2nd rolling piston 52, the 1st slide plate 53, the 2nd slide plate 54, bent axle 30, main bearing 43 and supplementary bearing 45.
1st cylinder 11 has the 1st compression chamber 11a, and the 2nd cylinder 21 has the 2nd compression chamber 21a.Central diaphragm 40 is between the 1st cylinder 11 and the 2nd cylinder 21.1st rolling piston 51 eccentric rotating is rotatably located in the 1st compression chamber 11a, and the 2nd rolling piston 52 eccentric rotating is rotatably located in the 2nd compression chamber 21a.1st slide plate 53 and the 1st rolling piston 51 synchronous reciprocating slide.2nd slide plate 54 and the 2nd rolling piston 52 synchronous reciprocating slide.
Bent axle 30 comprises the 1st torque-transmitting axle 34, the 2nd torque-transmitting axle 35, main shaft 31 and countershaft 33.1st torque-transmitting axle 34 drives the 1st rolling piston 51 eccentric rotary, and the 2nd torque-transmitting axle 35 drives the 2nd rolling piston 52 eccentric rotary.Main shaft 31 and main bearing 43 are slidably matched, and countershaft 33 and supplementary bearing 45 are slidably matched.
At least one and bent axle 30 in 1st torque-transmitting axle 34 and the 2nd torque-transmitting axle 35 are separated and assembled, be that the 1st torque-transmitting axle 34 of separated and assembled and/or the 2nd torque-transmitting axle 35 can coordinate for being slidably matched or being pressed into bent axle 30 with bent axle 30, and bent axle 30 is the 1st torque-transmitting axle 34 of separated and assembled and/or is provided with transmission of torque part between the 2nd torque-transmitting axle 35 and bent axle 30.Such as, the 1st torque-transmitting axle 34 is separated and assembled with bent axle 30, when installing twin-tub rotation-type compressor 1, first main shaft 31 being passed central diaphragm 40, and then being installed on main shaft 31 by the 1st torque-transmitting axle 34.Thus being formed in one compared with formula with the 1st traditional torque-transmitting axle and the 2nd torque-transmitting axle and bent axle, the central diaphragm internal diameter of central diaphragm 40 of the present invention can reduce, and can increase the path increment of slide plate.
According to the twin-tub rotation-type compressor 1 of the embodiment of the present invention, be slidably matched by least one making the 1st torque-transmitting axle 34 and the 2nd torque-transmitting axle 35 with bent axle 30 or be pressed into and coordinate, therefore the core shift amount of bent axle 30 can be increased, the design freedom of compression chamber, rolling piston and slide plate etc. expands, and can carry out the design improving compression efficiency.
In some embodiments of the invention, transmission of torque part is key or moment rod.That is, bent axle 30 can be transmitted torque on the 1st torque-transmitting axle 34 and/or the 2nd torque-transmitting axle 35 by key or moment rod.
According to some embodiments of the present invention, when the 1st torque-transmitting axle 34 with bent axle 30 for being separated assembling time, namely when the 1st torque-transmitting axle 34 is slidably matched with bent axle 30 or be pressed into coordinate time, central diaphragm internal diameter is larger than the external diameter of main shaft 31 and less than the external diameter of the 1st torque-transmitting axle 34.And/or, when the 2nd torque-transmitting axle 35 with bent axle 30 for being separated assembling time, namely the 2nd torque-transmitting axle 35 is slidably matched with bent axle 30 or is pressed into when coordinating, and central diaphragm internal diameter is larger than the external diameter of countershaft 33 and less than the external diameter of the 2nd torque-transmitting axle 35.
In some embodiments of the invention, the external diameter of countershaft 33 is less than the external diameter of main shaft 31.
In some embodiments of the invention, central diaphragm 40 is the thrust slip surface supporting bent axle 30 load.
According to some embodiments of the present invention, the 1st torque-transmitting axle 34 is slidably matched with bent axle 30 or is pressed into and coordinates, and the axial action amplitude of the 1st torque-transmitting axle 34 is limited by central diaphragm 40 and main bearing 43; And/or
2nd torque-transmitting axle 35 is slidably matched with bent axle 30 or is pressed into and coordinates, and the axial action amplitude of the 2nd torque-transmitting axle 35 is limited by central diaphragm 40 and supplementary bearing 45.
Particularly, and bent axle 30 be slidably matched or be pressed into the 1st torque-transmitting axle 34 of cooperation and/or the 2nd torque-transmitting axle 35 is sintered alloy parts or is forged into shaped piece.
Embodiment 1:
Twin-tub rotation-type compressor 1 shown in Fig. 1, the periphery securing motor 4 in the internal diameter of cylindrical housings 2 and the periphery of main bearing 43 possessed in compression mechanical part 5.Compression mechanical part 5 comprises and is connected to the 1st cylinder 11 of the central diaphragm 40 that centre possesses and the 2nd cylinder 21 and bent axle 30 each via 5 screws and slides the main bearing 43 and supplementary bearing 45 supported.1st cylinder 11 and the 2nd cylinder 21 have the 1st sucking pipe 55 and the 2nd sucking pipe 56 respectively.These two sucking pipes are connected to liquid-storage container 60.At the rotor 4a of bent axle 30 fixed electrical machinery 4.
Shown in Fig. 2 is the cross section of compression mechanical part 5.The 1st rolling piston 51 possessed in the 1st compression chamber 11a formed respectively in 1st cylinder 11 and the 2nd cylinder 21 and the 2nd compression chamber 21a and the 2nd rolling piston 52 are driven by the 1st torque-transmitting axle 34 of bent axle 30 and the 2nd torque-transmitting axle 35, carry out eccentric rotary.
Further, by the eccentric rotary of the 1st rolling piston 51 and the 2nd rolling piston 52, the 1st slide plate 53 and the 2nd slide plate 54 move back and forth.At the 1st compression chamber 11a and the 2nd compression chamber 21a by the gas compressed, be discharged to the 1st baffler 43a and the 2nd baffler 45a respectively.But the venting gas appliance possessed in main bearing 43 and supplementary bearing 45 is not shown.
In embodiment 1, the size of compression chamber of 2 groups and the outside dimension of torque-transmitting axle and core shift amount same, the discharge capacity of two cylinders is same.But, when 2 grades of compressions and volume controlled etc., there is no need to allow the core shift amount of 2 torque-transmitting axles the same with the discharge capacity of compression chamber.
Bent axle 30 by: by the main shaft 31 of main bearing 43 sliding support, drive the 1st torque-transmitting axle 34 of the 1st rolling piston 51, being formed by the countershaft 33 of supplementary bearing 45 sliding support, the jack shaft 32 that links the 1st torque-transmitting axle 34 and the 2nd torque-transmitting axle 35 of driving the 2nd torque-transmitting axle 35 of the 2nd rolling piston 52, the 2nd torque-transmitting axle 35 to be driven by key 36.The central diaphragm internal diameter 40a of the through central diaphragm 40 of jack shaft 32.
The same with common twin-tub rotation-type compressor, the 1st torque-transmitting axle 34 is relative in the phase place of 180 degree with the 2nd torque-transmitting axle 35.The feature of embodiment 1 is, the 1st torque-transmitting axle 34 and bent axle 30 are integrated, but the 2nd torque-transmitting axle 35 and countershaft 33 are combined in sense of rotation by key 36, allows the transmission of torque of bent axle 30 on the 2nd torque-transmitting axle 35.
Related description is carried out to the main points of compression mechanical part 5 assembling method.First, the center hole aligning of the 1st cylinder 11 and main bearing 43, fixes with 5 screw 43b.Then, in the main shaft 31 of bent axle 30 vane slot that inserts the 1st cylinder 11 respectively by main bearing the 43,1st slide plate 53 and the 1st rolling piston 51 and the 1st compression chamber 11a.Afterwards, allow and there is no the countershaft 33 of the 2nd torque-transmitting axle 35 by the central diaphragm internal diameter 40a of the central diaphragm 40 shown in Fig. 3, be placed in the plane of the 1st cylinder 11.At this moment, notice that jack shaft 32 and central diaphragm internal diameter 40a do not come in contact.
Then, at keyway 33a (as shown in Figure 5) sunk key 36 of countershaft 33.Make key 36 consistent with the keyway 35e of the 2nd torque-transmitting axle 35, in the external diameter of countershaft 33, embed the internal diameter 35b (as shown in Figure 6) of the 2nd torque-transmitting axle 35.Afterwards, the 2nd cylinder 21 is placed on central diaphragm 40, configuration the 2nd rolling piston 52 and the 2nd slide plate 54.Further, the external diameter of countershaft 33 and the internal diameter 35b of the 2nd torque-transmitting axle 35 have being slidably matched or the interference fit of lighter pressure of a little gap.
Further, aligning countershaft 33 and supplementary bearing 45, supplementary bearing 45 and the 2nd cylinder 21 fix with 5 screw 45b.At this moment, because screw 45b is the screw hole by the 2nd cylinder 21 and central diaphragm 40, central diaphragm 40 is clipped between two cylinders to fix.The assembling of compression mechanical part 5 just can follow assembling procedure in the past like this.
Thrust clearance C shown in Fig. 2 is, the gap of the junction plane of the 1st thrust top 34a that the 1st torque-transmitting axle 34 has and main bearing 43 and the 1st cylinder 11.Such as 0.3 ~ 1.0mm.Due to the scope that this gap is the knee-action determining the bent axle 30 integrated with rotor 4a (Fig. 1), so will note not allowing above-mentioned thrust clearance C excessive.The knee-action of bent axle 30 happens occasionally in compressor transport, but can not occur in the running.
On the other hand, in embodiment 1, the 2nd torque-transmitting axle 35 is the loads being born bent axle 30 by the lower end of jack shaft 32, and the 2nd thrust 35a had in the lower end of the 2nd torque-transmitting axle 35 is the conventional design that the load supporting bent axle 30 rotates.This design, after the upper end of the 2nd torque-transmitting axle 35 has added the thrust surface same with the 2nd thrust 35a, has reduced the gap of central diaphragm 40 and the 2nd torque-transmitting axle 35.That is, if make the height of the 2nd torque-transmitting axle 35 consistent with the height of the 2nd cylinder 21, the knee-action of the 2nd torque-transmitting axle 35 just without.
The present invention is, below in operation owing to embedding the 2nd torque-transmitting axle at countershaft 33, central diaphragm internal diameter 40a is roughly the same with the outside dimension of jack shaft 32, and the size of design comparison central diaphragm internal diameter 40a in the past significantly reduces.Its result, central diaphragm internal diameter 40a and minimum clearance size (w) of carrying out being formed between the external diameter of the 1st rolling piston 51 revolved round the sun become large.
Embodiment 1, relative to the external diameter of main shaft 31, the reduced diameter of countershaft 33, adopts so-called size axle.Size axle is normally relative to main shaft external diameter, and countershaft external diameter reduces in the scope of 10 ~ 15%.Such as, main shaft 31 is 18mm, and the external diameter of countershaft 33 is exactly 16mm.Further, the external diameter of jack shaft 32 can select between main shaft 31 and the size of countershaft 33.
At this, design (left figure) equal to central diaphragm internal diameter the as usual and 2nd torque-transmitting axle in the diagram, and the design (right figure) equal with 16mm (countershaft footpath) according to embodiment 1, possible maximum core shift amount (e) is compared.
Designed (left figure) is in the past, due to central diaphragm internal diameter (40a, dotted line) and torque-transmitting axle external diameter roughly equal, so need increasing rolling piston internal-and external diameter to guarantee minimum clearance size (w1).Therefore, the path increment S1 of slide plate (54) reduces.On the other hand, because embodiment 1 (right figure) central diaphragm internal diameter 40a and countershaft external diameter are roughly equal, thus minimum clearance size (w2) is enough large.Thus, due to rolling piston internal-and external diameter can be reduced, the path increment S2 of slide plate 54 therefore can be allowed to increase.Further, slide plate path increment (S) is 2 times of core shift amount (e) of torque-transmitting axle.
After expanding the core shift amount of twin-tub rotation-type compressor, design freedom adds.Such as, by core shift amount, cylinder height internal diameter, or the combination of the diameter of axle etc., can carry out raising the efficiency and improving reliability, and take into account the design of these two aspects.Further, also transfiguration is easy in the expansion of refrigerating capacity.That is, the expansion of core shift amount range of choice is indispensable factor for twin-tub rotation-type compressor.
In addition, because central diaphragm internal diameter 40a after w<0 is perforate in the 1st compression chamber 11a and the 2nd compression chamber 21a, so be full of pressurized gas and the oil of the 1st rolling piston 51 internal diameter, there is the problem flowed out in 2 lower compression chambers of pressure.That is, not only compression mechanical part efficiency significantly reduces, and because the most of oil in the axle by bent axle 30 has flowed out to 2 compression chambers, therefore compressor can not fuel feeding, can produce fault at short notice.
Fig. 5 is the details drawing of bent axle 30, represents and is assembled in the 2nd torque-transmitting axle 35 of countershaft 33, the configuration of oil groove 35c and oilhole 35d.The position of the keyway 33a had on countershaft 33 is represented relative to Fig. 6 of Fig. 5 90-degree rotation.Axle center hole 30a is provided in the oil supply gallery on bent axle 30 axle center.
Figure 7 shows that the 2nd detailed torque-transmitting axle 35 and key 36.The keyway 35e had at the center of internal diameter 35b is semi-cylindrical groove, has received the about columniform key 36 of half.Remaining half is in the semi-cylindrical keyway 33a of processing in the countershaft 33 being accommodated in Fig. 6.
Key 36 inserts fixing at the keyway 33a of countershaft 33, and afterwards, if the keyway 35e of the 2nd torque-transmitting axle 35 inserts countershaft 33 along key 36, key 36 is accommodated in keyway 33a and keyway 35e, and countershaft 33 and the 2nd torque-transmitting axle 35 are combined closely in sense of rotation.Further, because the length of keyway 35e is slightly longer than the length of key 36, they combine rear countershaft 33 and can move up and down in the amplitude range of about the 1mm of the axis of countershaft 33.By the knee-action fluctuation of the bent axle 30 when this gap Absorbable rod assembly error and conveying.
In embodiment 1, the keyway 35e only inserting the 2nd torque-transmitting axle 35 towards the key 36 of keyway 33a being accommodated in countershaft 33 completes assembling.Its reason is limited by the 1st above-mentioned thrust top 34a and the 2nd thrust 35a according to the dynamic up and down of the 2nd torque-transmitting axle 35.Further, the design alternative of key and keyway has a lot of method, as shown in JISB1310 etc.
Then, the material of the 2nd torque-transmitting axle 35 and manufacture method aspect, adopt and the same material of bent axle 30, such as: the method for processing with FCD500 (nodular cast iron), or by the method for sintered alloy and forging method manufacture.As material and the manufacture method of the 2nd torque-transmitting axle 35, if consider processing charges and wear resistance performance, sintered alloy (also saying it is sintered alloy) and forging method have superiority.Further, if words in need, in the middle of them, add wear-resisting consumptive material also easy.
Embodiment 2:
Embodiment 2 shown in Fig. 8 is, central diaphragm 40 utilizes as the thrust surface of bent axle 30.In order to achieve this end, jack shaft 32 is equal with the external diameter of the countershaft 33 after path, and central diaphragm internal diameter 40a is minimized.Its result, the thrust on the 2nd torque-transmitting axle 35 used in embodiment 1 and the surface of supplementary bearing 45, can be altered to thrust place of the 1st torque-transmitting axle 34 and central diaphragm 40.
The 1st thrust bottom 34b added in the lower end surface of the 1st torque-transmitting axle 34, supports the thrust load of bent axle 30, rotational slide in the plane of central diaphragm 40.The lubrication of the 1st thrust bottom 34b is, carrys out fuel feeding as in Example 1 by the oil groove that has in the 1st torque-transmitting axle 34 and oilhole.On the other hand, the 2nd thrust 35a of the 2nd torque-transmitting axle 35 is the loads not bearing bent axle 30, at the surface sliding of supplementary bearing 45.
By changing the thrust slip surface of bent axle 30 at central diaphragm 40 place, circular groove 46 can be added on supplementary bearing 45.Further, if the need arises, main bearing 43 adds the wear resistance performance that circular groove 46 can improve main shaft 31.Further, there are the words of circular groove 46 to reduce slide area at thrust slip surface, also have due to very difficult generation oil film, the abrasion in the face of thrust both sides can be made to become large.
Embodiment 3:
Fig. 9 and Figure 10 is illustrated respectively in bent axle 30 and the 2nd torque-transmitting axle 35 of embodiment 3 li use.Such a embodiment 3 is, as the substitute technology of the key 36 used in embodiment 1 and embodiment 2, uses moment rod 38.
Assembling method is, central diaphragm, by after the external diameter of countershaft 33, inserts circular moment rod 38 in the moment rod hole 33b laterally running through countershaft 33.Afterwards, in countershaft 33, insert the 2nd torque-transmitting axle 35 shown in Figure 10.At this moment, allow moment rod 38 consistent with moment rod groove 38b.The degree of depth of moment rod groove 38b is that the external diameter of torque gradient rod 38 is slightly dark.As above, be only used in countershaft 33 and insert the assembling that the 2nd torque-transmitting axle 35 just completes the 2nd torque-transmitting axle 35.
At this, in general design, insert spiral plate using as oil pump at axle center hole 30a.Thus, after inserting moment rod, just the problem of interference is had with above-mentioned spiral plate.But, just can deal with problems behind the hole that the interference position of this spiral plate adds by moment rod 38.
In order to the allocation position of moment rod hole 33b is consistent with external diameter immediate vicinity at the 2nd torque-transmitting axle 35 place.Arrange the through hole crossing with axis perpendicular from the external diameter of the 2nd torque-transmitting axle 35, insert the 2nd torque-transmitting axle 35 at countershaft 33, allow spring pin from the moment rod hole 33b of the through countershaft 33 of above-mentioned through hole, the design allowing the 2nd torque-transmitting axle and countershaft 33 combine also can be selected.Not only in the sense of rotation of countershaft 33 in this design, be also combine at axle direction the 2nd torque-transmitting axle 35 and countershaft 33.
Embodiment 4:
Above-mentioned 3 embodiments for the 2nd torque-transmitting axle 35 and countershaft 33 be separated formation, but embodiment 4 is that integration forms the 2nd torque-transmitting axle 35 and countershaft 33 as shown in figure 11.On the other hand, formation the 1st torque-transmitting axle and main shaft 31 is separated.
The assembling of compression mechanical part 5 and embodiment 1 equally can general equipment in the past.In advance, at the main shaft 31 that the central diaphragm internal diameter 40a of central diaphragm 40 inserts bent axle 30, in main shaft 31, the 1st torque-transmitting axle 34 is fixed.This is called that bent axle is assembled.On the other hand, aligning assembling main bearing 43 and the 1st cylinder 11, configure the 1st rolling piston 51 and the 1st slide plate 53 in the assigned position of the 1st cylinder 11.Afterwards, in the internal diameter of the 1st rolling piston 51 and the axis hole of main bearing 43, insert the main shaft 31 of above-mentioned crankshaft group.Operation afterwards and embodiment 1 same.
Embodiment 4 has central diaphragm internal diameter 40a can not be less than the shortcoming of the external diameter of main shaft 31, but owing to can reduce central diaphragm internal diameter 40a with design comparison in the past, likely allows the core shift amount of bent axle 30 increase.That is, if be separated at least one party of formation 2 torque-transmitting axles, just likely reducing central diaphragm internal diameter 40a increases core shift amount.
Because the present invention is mainly about the improvement of compression mechanical part, not only can be applicable to closed rotary compressor, also can be applicable to the opening rotary compressor of belt drives.Further, also can be applicable to horizontal dual cylinder rotary compressor and wave shape twin-tub rotation-type compressor.These twin-tub rotation-type compressors can be mounted in the devices such as air-conditioning, refrigerating machine, water heater, vehicle-mounted refrigeration or air-conditioning.
From upper description, the problem that the present invention will solve is:
Twin-tub rotation-type compressor, the central diaphragm center hole possessed between 2 cylinders is larger than the core shift diameter of axle of bent axle.Therefore the offset of torque-transmitting axle is had can not to do large problem.
In order to solve the concrete means that above-mentioned problem adopts:
2nd torque-transmitting axle is separated with countershaft 33.In the assembling procedure of compression mechanical part 5, countershaft 33 is by central diaphragm internal diameter 40a.Then, after countershaft 33 inserts the 2nd torque-transmitting axle 35, they are combined by key 36.Therefore, the rotational torque of bent axle 30 is delivered in the 2nd torque-transmitting axle 35.In addition, central diaphragm internal diameter 40a is equal with the external diameter of countershaft 33.Thus, the core shift amount of bent axle 30 can be increased.
Above-mentioned means are adopted to be the beneficial effect that the present invention brings:
(1) in twin-tub rotation-type compressor, because the core shift amount of bent axle increases, the expansion of compression element design freedom, achieves the design that efficiency improves.
(2) owing to can form the thrust surface of bent axle at central diaphragm, so at bearing looping groove, the reliability of bent axle can be improved.
(3) compressing mechanism assembling easily, and aligning assembling in the past can be general.Further, the increase of number of components is few.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification or example and different embodiment or example can carry out combining and combining by those skilled in the art.
Although illustrate and describe embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.
Claims (7)
1. a twin-tub rotation-type compressor, is characterized in that, comprising:
1st cylinder and the 2nd cylinder, described 1st cylinder has the 1st compression chamber, and described 2nd cylinder has the 2nd compression chamber;
Central diaphragm between described 1st cylinder and described 2nd cylinder;
The 1st rolling piston and the 2nd rolling piston of eccentric rotary is carried out respectively in described 1st compression chamber and described 2nd compression chamber;
The 1st slide plate slided with described 1st rolling piston and described 2nd rolling piston synchronous reciprocating respectively and the 2nd slide plate;
Bent axle, described bent axle comprise drive the 1st torque-transmitting axle of described 1st rolling piston and described 2nd rolling piston and the 2nd torque-transmitting axle respectively, the main shaft of the main bearing that is connected respectively with described 1st cylinder and described 2nd cylinder and supplementary bearing sliding support and countershaft;
At least one of described 1st torque-transmitting axle and described 2nd torque-transmitting axle is slidably matched with described bent axle or is pressed into cooperation, possesses transmission of torque part between which.
2. twin-tub rotation-type compressor according to claim 1, is characterized in that, described transmission of torque part is key or moment rod.
3. twin-tub rotation-type compressor according to claim 1, it is characterized in that, described 1st torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, and the central diaphragm internal diameter of described central diaphragm is greater than the external diameter of described main shaft and is less than the external diameter of described 1st torque-transmitting axle; And/or
Described 2nd torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, and the central diaphragm internal diameter of described central diaphragm is greater than the external diameter of described countershaft and is less than the external diameter of described 2nd torque-transmitting axle.
4. twin-tub rotation-type compressor according to claim 1, is characterized in that, the external diameter of described countershaft is less than the external diameter of described main shaft.
5. twin-tub rotation-type compressor according to claim 1, is characterized in that, described central diaphragm is the thrust slip surface supporting described bent axle load.
6. twin-tub rotation-type compressor according to claim 1, is characterized in that, described 1st torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, and the axial action amplitude of described 1st torque-transmitting axle is limited by described central diaphragm and described main bearing; And/or
Described 2nd torque-transmitting axle is slidably matched with described bent axle or is pressed into and coordinates, and the axial action amplitude of described 2nd torque-transmitting axle is limited by described central diaphragm and described supplementary bearing.
7. twin-tub rotation-type compressor according to claim 1, is characterized in that, and described 1st torque-transmitting axle that coordinates of described bent axle and/or described 2nd torque-transmitting axle are sintered alloy parts or are forged into shaped piece.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510599155.6A CN105114312A (en) | 2015-09-17 | 2015-09-17 | Double-cylinder rotating compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510599155.6A CN105114312A (en) | 2015-09-17 | 2015-09-17 | Double-cylinder rotating compressor |
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| Publication Number | Publication Date |
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| CN105114312A true CN105114312A (en) | 2015-12-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510599155.6A Pending CN105114312A (en) | 2015-09-17 | 2015-09-17 | Double-cylinder rotating compressor |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2019138184A (en) * | 2018-02-07 | 2019-08-22 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
| CN116557295A (en) * | 2023-05-14 | 2023-08-08 | 广州市德善数控科技有限公司 | Assembling structure of compressor crankshaft and compressor |
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| CN104978123A (en) * | 2015-06-29 | 2015-10-14 | 努比亚技术有限公司 | Screen division method and apparatus |
| CN105041650A (en) * | 2015-08-06 | 2015-11-11 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor |
| CN205036576U (en) * | 2015-09-17 | 2016-02-17 | 广东美芝制冷设备有限公司 | Double -cylinder rotary compressor |
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| JPH03222887A (en) * | 1990-01-25 | 1991-10-01 | Mitsubishi Heavy Ind Ltd | Two-cylindered rotary compressor |
| CN102900670A (en) * | 2012-08-31 | 2013-01-30 | 珠海格力电器股份有限公司 | Horizontal compressor with symmetrical double cylinders |
| CN104978123A (en) * | 2015-06-29 | 2015-10-14 | 努比亚技术有限公司 | Screen division method and apparatus |
| CN105041650A (en) * | 2015-08-06 | 2015-11-11 | 广东美芝制冷设备有限公司 | Double-cylinder rotary compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2019138184A (en) * | 2018-02-07 | 2019-08-22 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
| CN116557295A (en) * | 2023-05-14 | 2023-08-08 | 广州市德善数控科技有限公司 | Assembling structure of compressor crankshaft and compressor |
| CN116557295B (en) * | 2023-05-14 | 2024-05-31 | 广州市德善数控科技有限公司 | Assembling structure of compressor crankshaft and compressor |
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