CN204783676U - Rotary compressor and bent axle thereof - Google Patents
Rotary compressor and bent axle thereof Download PDFInfo
- Publication number
- CN204783676U CN204783676U CN201520479558.2U CN201520479558U CN204783676U CN 204783676 U CN204783676 U CN 204783676U CN 201520479558 U CN201520479558 U CN 201520479558U CN 204783676 U CN204783676 U CN 204783676U
- Authority
- CN
- China
- Prior art keywords
- bent axle
- loss
- equalizing orifice
- compressor
- weight equalizing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 230000002093 peripheral Effects 0.000 claims abstract description 6
- 238000004519 manufacturing process Methods 0.000 abstract description 6
- 230000005484 gravity Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 5
- 239000002184 metal Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 239000003507 refrigerant Substances 0.000 description 4
- 238000005096 rolling process Methods 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 239000002826 coolant Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 238000010205 computational analysis Methods 0.000 description 1
- 238000010192 crystallographic characterization Methods 0.000 description 1
- 230000004059 degradation Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006011 modification reaction Methods 0.000 description 1
- 230000001264 neutralization Effects 0.000 description 1
- 230000001360 synchronised Effects 0.000 description 1
Abstract
The utility model discloses a rotary compressor and bent axle thereof. The bent axle includes main shaft portion and forms the eccentric portion in main shaft portion, is equipped with the first heavy balancing hole that subtracts in the off -centre portion, firstly subtracts heavy balancing hole and upwards has a perfect understanding the up end of off -centre portion and have a perfect understanding the lower terminal surface of off -centre portion downwards, and the while is first to subtract the outer peripheral face that weighs the balancing hole and still have a perfect understanding off -centre. According to the utility model discloses an under the bent axle, can be at the offset that keeps the bent axle unchangeable prerequisite, lighten the eccentric quality of bent axle, reduce to use the rotary compressor's of this bent axle the eccentric inertial force of rotation, reduce the vibration and the noise of compressor, improve the long -time maintainability of compressor. And the reduction of rotatory eccentric inertial force, the weight of compressor inner equilibrium piece can be be convenient for alleviate or even the balancing piece avoided using to reduce compressor manufacturing cost, the balancing piece received in the time of can reducing to operate simultaneously gas resistance improves the efficiency of compressor.
Description
Technical field
The utility model relates to compressor field, especially relates to a kind of rotary compressor and bent axle thereof.
Background technique
For rotary compressor, its main working parts is the rolling piston be nested on eccentric crankshaft, when compressor electric motor in the energized state, drive rolling piston is done eccentric motion by the eccentric crankshaft be connected with rotor in pump body compression chamber, thus realizes compression to cold media air.This kind of mechanism due to structure simple, compression efficiency is high, is therefore widely used in various technical field of refrigeration equipment.
Owing to have employed eccentric rotary structure, not on the rotary shaft, therefore compressor is in the running by generation rotating inertia force for the center of gravity of running gear, and eccentric direction is pointed in its direction.The existence of eccentric inertial force can make the vibration of compressor rise, and affects vibration and the pipeline reliability of compressor and refrigeration system, also can bring noise problem, affect refrigeration system comfort.
For solving the problem, in the design of existing compressor, offset mass eccentricity at two ends of rotor configuration equilibrium block.Adopt such method effectively can reduce noise and the vibration of compressor, but be arranged on rotor due to equilibrium block, for avoiding the decline of electric efficiency, equilibrium block material magnetic conduction Capability Requirement is comparatively strict, causes equilibrium block cost of material higher.In addition, after rotor increases equilibrium block, in compressor operation process, equilibrium block will be subject to very large gas force effect, increase the running resistance of compressor, result in the decline of compressor efficiency, in the middle of compressor High Rotation Speed, equilibrium block creates comparatively Great inertia power even, and this inertial force acts on bent axle also to be increased the abrasion caused between bent axle and bearing.
There is the problem that equilibrium block quality is excessive, crankshaft eccentric inertial force causes more greatly reliability to reduce in the rotary compressor in correlation technique.Inventor finds through research and a large amount of experiments, and in compressor, the eccentric mass of eccentric movement component is excessive to cause the excessive reason of equilibrium block quality to be.Therefore, inventor finds, the inertial force of eccentric mass to reduction bent axle reducing eccentric movement component, the quality reducing equilibrium block have significant effect.
For this reason, the utility model aims to provide a kind of bent axle, and rotary compressor uses this bent axle, can be beneficial to the weight reducing equilibrium block in rotary compressor.
Another object of the present utility model is to provide a kind of rotary compressor with above-mentioned bent axle.
According to bent axle of the present utility model, described bent axle is used for rotary compressor, described bent axle comprises main shaft part and is formed in the eccentric part in described main shaft part, described eccentric part is provided with the first loss of weight equalizing orifice, the described first loss of weight equalizing orifice upwards upper-end surface of through described eccentric part and the lower end surface of downward through described eccentric part, the simultaneously outer circumferential face of described first loss of weight equalizing orifice also through described eccentric part.
According to bent axle of the present utility model, by arranging the first loss of weight equalizing orifice on eccentric part, thus keeping under the prerequisite that the offset of bent axle is constant, alleviate the eccentric mass of bent axle, shorten the distance of the deviation of gravity center rotating center axis of bent axle, reduce the rotating eccentricity inertial force of the rotary compressor using this bent axle simultaneously, reduce vibration and the noise of compressor, improve the reliability of compressor long time running.And the minimizing of rotating eccentricity inertial force, the weight can being convenient to alleviate compressor inner equilibrium block even avoids balance block, thus reduces Compressor Manufacturing cost, and air resistance when simultaneously can reduce to operate suffered by equilibrium block, improves the efficiency of compressor.
In certain embodiments, the outer circumferential face of described main shaft part is provided with multiple protruding structure, two adjacent described protruding structures limit a described first loss of weight equalizing orifice.Thus, the rotating eccentricity inertial force of the rotary compressor reducing this bent axle of use can be reached, reduce the vibration of compressor and the object of noise, also facilitate the weight alleviating compressor inner equilibrium block.
Particularly, the second loss of weight equalizing orifice is provided with in protruding structure described at least one.Thus, further can alleviate the eccentric mass of eccentric part, reduce the rotating eccentricity inertial force of the rotary compressor using this bent axle, reduce vibration and the noise of compressor, conveniently alleviate the weight of compressor inner equilibrium block.
Alternatively, the described second loss of weight equalizing orifice through hole that is eccentric part described in up/down perforation.Thus, the processing of the second loss of weight equalizing orifice is more convenient, and the cost of production of bent axle is lower, and the eccentric mass of eccentric part can significantly reduce.
Advantageously, bent axle also comprises: horizontal baffle, described horizontal baffle is orthogonal to the central axis of described main shaft part and is arranged in described second loss of weight equalizing orifice, and the inner peripheral surface of the outer circumferential face of described horizontal baffle and described second loss of weight equalizing orifice is fitted in the circumferential at least in part.Be provided with like this to be beneficial to and improve the rigidity in crankshaft eccentric portion, avoid eccentric part to be out of shape under the effect of pressurized gas power and excessively cause Leakage Gas, thus avoid reducing compressor efficiency.
More specifically, the hole structure that the inner bottom part that described horizontal baffle is arranged on described second loss of weight equalizing orifice opens wide to make described second loss of weight equalizing orifice be configured to top; Or the inner top that described horizontal baffle is arranged on described second loss of weight equalizing orifice is configured to the hole structure of bottom-open to make described second loss of weight equalizing orifice; Or described horizontal baffle respectively with the upper-end surface of described eccentric part and lower end surface spaced apart.
In further embodiments, the outer circumferential face of described main shaft part is provided with multiple connecting plate, the free end of each described connecting plate is provided with arc plate, and two adjacent connecting plates limit a described first loss of weight equalizing orifice.Thus, also can alleviate the eccentric mass of eccentric part to greatest extent, reach the rotating eccentricity inertial force of the rotary compressor reducing this bent axle of use, reduce the vibration of compressor and the object of noise, also facilitate the weight alleviating compressor inner equilibrium block.
Particularly, described first loss of weight equalizing orifice is positioned at the side of the central axis towards described eccentric part of the first longitudinal plane, and described first longitudinal plane is central axis by described main shaft part and is orthogonal to the plane of the line of centres of described main shaft part and described eccentric part.Thus, the center of gravity of eccentric part amesialityly to move towards the side, center of main shaft part as much as possible by by original, thus obviously shorten the distance of the deviation of gravity center rotating center axis of bent axle, the further rotating eccentricity inertial force reducing the rotary compressor using this bent axle, reduce vibration and the noise of compressor, conveniently alleviate the weight of compressor inner equilibrium block.
Further, described first loss of weight equalizing orifice is divided into two groups, and described two group of first loss of weight equalizing orifice is symmetrical about the second longitudinal plane of the line of centres by described main shaft part and described eccentric part.Namely, when the first loss of weight equalizing orifice is multiple, the center of gravity of eccentric part also can be made to be positioned at as far as possible on the second longitudinal plane.
According to the rotary compressor of the utility model embodiment, comprise the bent axle according to the utility model above-described embodiment.
Additional aspect of the present utility model and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present utility model.
Model utility content
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present utility model and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 is the structural representation of existing rotary compressor;
Fig. 2 is the sectional structure schematic diagram of the bent axle according to the utility model embodiment;
Fig. 3 is the cross-sectional schematic in Q-Q direction in edge in Fig. 2;
Fig. 4 is the sectional structure schematic diagram of the bent axle according to the utility model embodiment;
Fig. 5 is the cross-sectional schematic in R-R direction in edge in Fig. 4;
Fig. 6 is the sectional structure schematic diagram of the bent axle according to the utility model embodiment;
Fig. 7 is the sectional structure schematic diagram of the bent axle according to another embodiment of the utility model;
Fig. 8 is the sectional structure schematic diagram of the bent axle according to the utility model embodiment;
Fig. 9 is the cross-sectional schematic in T-T direction in edge in Fig. 8.
Reference character:
100: rotary compressor;
1: exhaust manifolds; 2: upper shell; 3: main casing; 4: stator; 5: rotor; 6: bent axle; 60: center oil through; 61: main shaft part; 62: eccentric part; 7: upper bearing (metal); 8: cylinder; 9: lower bearing; 10: lower shell body; 11: slide plate; 12: piston; 120: center hole; 13: equilibrium block; 14: liquid-storage container;
A: housing; B: motor; C: compressing mechanism; V: receiving cavity;
S1: the upper-end surface of eccentric part; S2: the lower end surface of eccentric part; S3: the outer circumferential face of eccentric part;
L1: the central axis of main shaft part; L2: the central axis of eccentric part; P1P2: the first longitudinal plane; P3P4: the second longitudinal plane; E: the offset of bent axle; O1: the central point on the cross section of main shaft part; O2: the central point on the cross section of eccentric part;
67: the first loss of weight equalizing orifices; 68: protruding structure; 69: the second loss of weight equalizing orifices; 65: horizontal baffle;
621: connecting plate; 622: arc plate.
Embodiment
Be described below in detail embodiment of the present utility model, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the utility model, and can not be interpreted as restriction of the present utility model.
In description of the present utility model, it will be appreciated that, term " " center ", " highly ", " width ", " thickness ", " on ", D score, " vertically ", " level ", " top ", " end ", " interior ", " outward ", " 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 utility model and simplified characterization for convenience of description, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as restriction of the present utility model.
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 one or more these features.In description of the present utility model, except as otherwise noted, the implication of " multiple " is two or more.
In description of the present utility model, unless otherwise clearly defined and limited, 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; 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.For the ordinary skill in the art, concrete condition the concrete meaning of above-mentioned term in the utility model can be understood.
In the utility model, unless otherwise clearly defined and limited, fisrt feature second feature it " on " or D score can comprise the first and second features and directly contact, also can comprise the first and second features and not be directly contact but by the other characterisation contact between them.And, fisrt feature second feature " on ", " top " and " above " comprise fisrt feature directly over second feature and oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " comprise fisrt feature immediately below second feature and tiltedly below, or only represent that fisrt feature level height is less than second feature.
Describe the bent axle 6 according to the utility model embodiment below with reference to Fig. 1-Fig. 9, bent axle 6 is for rotary compressor 100.
Particularly, as shown in Figure 1, rotary compressor 100 comprises: housing A, motor B and compressing mechanism C.Housing A is seal container, limits receiving cavity V in housing A, and motor B and compressing mechanism C is all located in receiving cavity V.In the example illustrated in figure 1, housing A comprises main casing 3, upper shell 2 and lower shell body 10, and main casing 3 is formed as the tubular of upper and lower both ends open, and upper shell 2 and lower shell body 10 are located at the two ends up and down of main casing 3 respectively.Rotary compressor 100 also comprises exhaust manifolds 1, and exhaust manifolds 1 to be located on housing A and to be communicated with receiving cavity V, and in the example of fig. 1, exhaust manifolds 1 are connected on upper shell 2.
As shown in Figure 1, motor B comprises stator 4 and coordinates the rotor 5 rotated with stator 4.In the example of fig. 1, motor B is inner rotor motor, is namely enclosed within rotor 5 outside stator 4.
As shown in Figure 1, compressing mechanism C comprises bent axle 6, cylinder assembly, lower bearing 9, upper bearing (metal) 7, piston 12 and slide plate 11 etc., and cylinder assembly can comprise one or more cylinder 8.Wherein, bent axle 6 runs through cylinder assembly and is enclosed within outside rotor 5 on bent axle 6, bent axle 6 be fixedly connected with rotor 5 with rotor 5 synchronous rotary.Upper bearing (metal) 7 and lower bearing 9 are located at the two ends up and down of cylinder assembly respectively, upper bearing (metal) 7 and/or lower bearing 9 are provided with the exhaust port (scheming not shown) being communicated with cylinder interior space, and bent axle 6 coordinates to be located at rotationally in housing A with upper bearing (metal) 7 and lower bearing 9 respectively.Be located in cylinder 8 to piston 12 eccentric rotary, bent axle 6 is connected with piston 12 with driven plunger 12 eccentric rotary, and bent axle 6 drive piston 12 rotate and compression cylinder 8 in refrigerant.Rotary compressor 100 also provides refrigerant to be compressed by liquid-storage container 14, and liquid-storage container 14 is connected with cylinder 8.Cylinder interior space is divided into hyperbaric chamber and low-pressure cavity by slide plate 11, compression refrigerant in piston 12 rotation process, and the pressure in hyperbaric chamber is raised, and when pressure is increased to the pressure outside slightly larger than compressing mechanism C, namely pressurized gas refrigerant discharges by exhaust port.
Wherein, piston 12 is provided with center hole 120, the eccentric part 62 that bent axle 6 comprises main shaft part 61 and is formed in main shaft part 61, and the eccentric part 62 of bent axle 6 coordinates with the center hole 120 of piston 12.Crankshaft eccentric portion 62 is formed as round column structure usually, and the central axis L2 in crankshaft eccentric portion 62 is parallel to the central axis L1 of main shaft part 61, and the perpendicular distance of L1 and L2 is the eccentric amount e of bent axle 6.Wherein, the central axis L1 of main shaft part 61 is also the spin axis of bent axle 6.In some instances, main shaft part 61 is also provided with center oil through 60, center oil through 60 is located on the central axis L1 of main shaft part 61 usually, the through in the axial direction main shaft part 61 of center oil through 60.
Be eccentric system due to bent axle 6 and by the piston 12 of bent axle 6 driven rotary, larger vibration can be caused during rotation, therefore in the design, usually also need at the two ends of rotor 5 configuration equilibrium block 13 to offset mass eccentricity.
According to the bent axle 6 of the utility model embodiment, as shown in Figures 2 and 3, eccentric part 62 is provided with the first loss of weight equalizing orifice 67, the first loss of weight equalizing orifice 67 upwards upper-end surface S1 of through eccentric part 62 and the lower end surface S2 of downward through eccentric part 62, simultaneously the outer circumferential face S3 of the first loss of weight equalizing orifice 67 also through eccentric part 62.That is, the setting of the first loss of weight equalizing orifice 67 is equivalent to, in crankshaft eccentric portion disclosed in prior art, inwardly cut out a part of material along eccentric part periphery.
By arranging the first loss of weight equalizing orifice 67 on eccentric part 62, the weight of the eccentric part 62 of bent axle 6 is alleviated greatly, thus the rotating eccentricity inertial force of the rotary compressor 100 using this bent axle 6 can be reduced, reach the object reducing vibration of compressor, noise, improve the reliability of compressor long time running.And the minimizing of rotating eccentricity inertial force, the weight can being convenient to reduce compressor inner equilibrium block 13 even avoids balance block 13, thus reducing Compressor Manufacturing cost, air resistance when simultaneously can reduce to operate suffered by equilibrium block 13, reaches the object improving compressor efficiency.
According to the bent axle 6 of the utility model embodiment, by arranging the first loss of weight equalizing orifice 67 on eccentric part 62, thus keeping under the prerequisite that the eccentric amount e of bent axle 6 is constant, alleviate the eccentric mass of bent axle 6, shorten the distance of the deviation of gravity center rotating center axis of bent axle 6, thus reduce the rotating eccentricity inertial force of the rotary compressor 100 using this bent axle 6, reduce vibration and the noise of compressor, improve the reliability of compressor long time running.And the minimizing of rotating eccentricity inertial force, the weight can being convenient to alleviate compressor inner equilibrium block 13 even avoids balance block 13, thus reducing Compressor Manufacturing cost, air resistance when simultaneously can reduce to operate suffered by equilibrium block 13, improves the efficiency of compressor.
Particularly, as shown in Figures 2 and 3, first loss of weight equalizing orifice 67 is positioned at the side of the central axis L2 towards eccentric part 62 of the first longitudinal plane P1P2, here, the first longitudinal plane P1P2 is central axis L1 by main shaft part 61 and is orthogonal to the plane of main shaft part 61 and the line of centres of eccentric part 62.
Wherein, as shown in Figure 3, on arbitrary cross section of bent axle 6, the central point of main shaft part 61 is O1, and the central point of eccentric part 62 is O2, and the first longitudinal plane P1P2 is perpendicular to O1O2 line.
The side of the central axis L2 towards eccentric part 62 of the first longitudinal plane P1P2 is positioned at due to the first loss of weight equalizing orifice 67, the center of gravity of eccentric part 62 moves towards the O1 side, center of main shaft part 61 as much as possible by by original deflection O2 side, thus obviously shorten the distance of the deviation of gravity center rotating center axis of bent axle 6, the further rotating eccentricity inertial force reducing the rotary compressor 100 using this bent axle 6, reduce vibration and the noise of compressor, conveniently alleviate the weight of compressor inner equilibrium block 13.
Particularly, as shown in Figure 3, the first loss of weight equalizing orifice 67 is symmetrical about the second longitudinal plane P3P4 by the central axis L1 of the main shaft part 61 and central axis L2 of eccentric part 62, and wherein, the second longitudinal plane P3P4 is perpendicular to the first longitudinal plane P1P2.Thus, the center of gravity of eccentric part 62 can be made to be positioned on the second longitudinal plane P3P4.It should be noted that, for determining the weight and the mounting point that need the equilibrium block 13 installed, computational analysis is needed to go out center of mass's point of bent axle 6, therefore the center of gravity of eccentric part 62 is located on the second longitudinal plane P3P4, the amount of calculation of bent axle 6 center of mass's point can be reduced, be convenient to the whole machine balancing analysis of compressor eccentric system.
Below with reference to Fig. 2-Fig. 9, multiple specific embodiment is described, so that understand the concrete structure of the bent axle 6 of the utility model embodiment in detail.Wherein, in different embodiments, identical label shows identical parts or has the parts of identical function.
Embodiment one
In this embodiment, as shown in Figures 2 and 3, the outer circumferential face of main shaft part 61 is provided with multiple protruding structure 68, two adjacent protruding structures 68 limit a first loss of weight equalizing orifice 67.That is, bent axle 6 is coordinated with piston 12 by multiple protruding structure 68, in other words, the outer circumferential face S3 of eccentric part 62 is divided into multiple arc surface, multiple arc surface contacts with the inner peripheral surface of piston 12 and coordinates, and like this, alleviates the eccentric mass of eccentric part 62 to greatest extent, reach the rotating eccentricity inertial force of the rotary compressor 100 reducing this bent axle 6 of use, reduce the vibration of compressor and the object of noise, also facilitate the weight alleviating compressor inner equilibrium block 13.
In embodiment one, by arranging multiple first loss of weight equalizing orifice 67, the outer circumferential face S3 being positioned at the side of the central axis L2 towards eccentric part 62 of the first longitudinal plane P1P2 of eccentric part 62 is at least divided into three sections of arc surfaces.
In addition, because the outer circumferential face S3 of eccentric part 62 is made up of multi-section circular arc face, like this when each arc surface circumferential lengths is all less, still the accurate location between crankshaft eccentric portion 62 and rolling piston 12 can be ensured, reach the area increasing the first loss of weight equalizing orifice 67 further, reduce the object of eccentric part 62 eccentric mass simultaneously.
Particularly, the first loss of weight equalizing orifice 67 is divided into two groups, and two group of first loss of weight equalizing orifice 67 is symmetrical about the second longitudinal plane P3P4 by the central axis L1 of the main shaft part 61 and central axis L2 of eccentric part 62.Like this, when the first loss of weight equalizing orifice 67 is multiple, the center of gravity of eccentric part 62 also can be made to be positioned at as far as possible on the second longitudinal plane P3P4.
Particularly, the shape of cross section of the first loss of weight equalizing orifice 67 can be fan-shaped or other are irregularly shaped, the shape of cross section of multiple first loss of weight equalizing orifice 67 can identical also can be different, also can be the combination of any several shape, not do concrete restriction here.Wherein, the cross section of the first loss of weight equalizing orifice 67 refers to the cross section profile that the plane perpendicular to the central axis L1 of main shaft part 61 is formed on the first loss of weight equalizing orifice 67.
In embodiment one, along on the central axis L1 direction of main shaft part 61, each shape of cross section, the sectional area of the first loss of weight equalizing orifice 67 can be identical, each shape of cross section, the sectional area of the first loss of weight equalizing orifice 67 also can be different, as long as can necessarily regulate eccentric part 62 rigidity in the axial direction, simultaneously can take into account bent axle 6 loss of weight and Deformation control requires, not do concrete restriction here.Such as, the sectional area of the cross section of the first loss of weight equalizing orifice 67 first diminishes from top to bottom, rear change is large, the sectional area of the cross section of the first loss of weight equalizing orifice 67 also can first become greatly from top to bottom, after diminish.Again such as, the sectional area of the cross section of the first loss of weight equalizing orifice 67 diminishes from top to bottom gradually, or the sectional area of the cross section of the first loss of weight equalizing orifice 67 becomes large from top to bottom gradually.More even, each shape of cross section of the first loss of weight equalizing orifice 67, size are by irregular mode change.
In addition, in embodiment one, the total volume of multiple first loss of weight equalizing orifice 67 and the ratio of eccentric part 62 volume are more than or equal to 8%.
Embodiment two
In this embodiment, as shown in Figure 4 and Figure 5, the structure of bent axle 6 is substantially identical with bent axle 6 structure in enforcement one, and this repeats no more.
Difference is, in embodiment two, the second loss of weight equalizing orifice 69 is provided with at least one protruding structure 68, thus, further can alleviate the eccentric mass of eccentric part 62, reduce the rotating eccentricity inertial force of the rotary compressor 100 using this bent axle 6, reduce vibration and the noise of compressor, conveniently alleviate the weight of compressor inner equilibrium block 13.
Particularly, the shape of cross section of the second loss of weight equalizing orifice 69 can be square, circular, crescent shape or fan-shaped, and the cross section of the second loss of weight equalizing orifice 69 also can be other shapes.Second loss of weight equalizing orifice 69 can be multiple, the shape of cross section of multiple second loss of weight equalizing orifice 69 can identical also can be different, also can be the combination of any several shape, not do concrete restriction here.
Certainly, the cross sectional area of the second loss of weight equalizing orifice 69 and quantity should carry out appropriate design according to the rigidity in crankshaft eccentric portion 62 and loss of weight composite request.
Wherein, the second loss of weight equalizing orifice 69 can be the through hole of up/down perforation eccentric part 62.Thus, the processing of the second loss of weight equalizing orifice 69 is more convenient, and the cost of production of bent axle 6 is lower, and the eccentric mass of eccentric part 62 can significantly reduce.
Again as shown in Figure 6 and Figure 7, bent axle 6 also can comprise horizontal baffle 65, horizontal baffle 65 is orthogonal to the central axis L1 of main shaft part 61 and is arranged in the second loss of weight equalizing orifice 69, and the inner peripheral surface of the outer circumferential face of horizontal baffle 65 and the second loss of weight equalizing orifice 69 is fitted in the circumferential at least in part.Horizontal baffle 65 is supported on eccentric part 62 and is formed on the thin-walled of the second loss of weight equalizing orifice 69, be provided with the rigidity being beneficial to and improving bent axle 6 eccentric part 62 like this, avoid eccentric part 62 to be out of shape under the effect of pressurized gas power and excessively cause Leakage Gas, thus avoid reducing compressor efficiency.
In embodiment two, as shown in Figure 6 and Fig. 7, horizontal baffle 65 is arranged on the inner bottom part of the second loss of weight equalizing orifice 69, the hole structure being configured to top to make the second loss of weight equalizing orifice 69 and opening wide.Horizontal baffle 65 also can be arranged on the inner top of the second loss of weight equalizing orifice 69, with the hole structure making the second loss of weight equalizing orifice 69 be configured to bottom-open.Horizontal baffle 65 also can be spaced apart with the upper-end surface S1 of eccentric part 62 and lower end surface S2 respectively, and namely horizontal baffle 65 is located at the neutral position of the second loss of weight equalizing orifice 69.
In addition, horizontal baffle 65 can arrange other structures, such as, horizontal baffle 65 can be provided with the oilhole (scheming not shown) of through horizontal baffle 65, thus be convenient to the lubrication of bent axle 6, reduce the frictional loss between bent axle 6 and piston 12.
Embodiment three
In this embodiment, as shown in Figure 8 and Figure 9, the outer circumferential face of main shaft part 61 is provided with multiple connecting plate 621, the free end of each connecting plate 621 is provided with arc plate 622, and two adjacent connecting plates 621 limit a first loss of weight equalizing orifice 67.That is, that is, bent axle 6 is coordinated with piston 12 by multiple arc plate 622, in other words, the outer circumferential face S3 of eccentric part 62 is divided into multiple arc surface, and multiple arc surface contacts with the inner peripheral surface of piston 12 and coordinates, like this, also can alleviate the eccentric mass of eccentric part 62 to greatest extent, reach the rotating eccentricity inertial force of the rotary compressor 100 reducing this bent axle 6 of use, reduce the vibration of compressor and the object of noise, also facilitate the weight alleviating compressor inner equilibrium block 13.
In embodiment three, by arranging multiple first loss of weight equalizing orifice 67, the outer circumferential face S3 being positioned at the side of the central axis L2 towards eccentric part 62 of the first longitudinal plane P1P2 of eccentric part 62 is at least divided into three sections of arc surfaces.
In addition, because the outer circumferential face S3 of eccentric part 62 is made up of multi-section circular arc face, like this when each arc surface circumferential lengths is all less, still the accurate location between crankshaft eccentric portion 62 and rolling piston 12 can be ensured, reach the area increasing the first loss of weight equalizing orifice 67 further, reduce the object of eccentric part 62 eccentric mass simultaneously.
According to the rotary compressor 100 of the utility model embodiment, comprise the bent axle 6 according to the utility model above-described embodiment.Wherein, bent axle 6 can be provided with single eccentric part 62, bent axle 6 also can be provided with multiple eccentric part 62.
Particularly, in certain embodiments, rotary compressor 100 is single stage compressor, single stage compressor comprises: crankshaft and piston 12, bent axle is the bent axle 6 according to the utility model above-described embodiment, the single eccentric part 62 that bent axle 6 comprises main shaft part 61 and is formed in main shaft part 61, eccentric part 62 is engaged in the center hole 120 of piston 12.
Owing to being provided with above-mentioned bent axle 6, namely on eccentric part 62, the first loss of weight equalizing orifice 67 is provided with, the rotating eccentricity inertial force of rotary compressor 100 can be reduced, be convenient to the weight reducing equilibrium block 13, reduce vibration of compressor and noise simultaneously, improve the reliability of compressor long time running, also can effectively prevent the coolant leakage in exhaust port and the degradation problem that causes.
In further embodiments, rotary compressor 100 is multistage compressor, and multistage compressor comprises: bent axle and multiple piston 12.Wherein, bent axle is the bent axle 6 according to the utility model above-described embodiment, multiple eccentric parts 62 that bent axle 6 comprises main shaft part 61 and is formed in main shaft part 61, and multiple eccentric part 62 is engaged in the center hole 120 of multiple piston 12 correspondingly.In multiple eccentric part 62, at least one eccentric part 62 is provided with the first loss of weight equalizing orifice 67, the rotating eccentricity inertial force of multistage compressor can be reduced, be convenient to the weight reducing equilibrium block 13, reduce vibration of compressor and noise simultaneously, improve the reliability of compressor long time running, also can effectively prevent the coolant leakage in exhaust port and the hydraulic performance decline that causes.
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 utility model or example.In this manual, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although illustrate and described embodiment of the present utility model, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present utility model and aim, scope of the present utility model is by claim and equivalents thereof.
Claims (10)
1. a bent axle, described bent axle is used for rotary compressor, it is characterized in that, described bent axle comprises main shaft part and is formed in the eccentric part in described main shaft part, described eccentric part is provided with the first loss of weight equalizing orifice, the described first loss of weight equalizing orifice upwards upper-end surface of through described eccentric part and the lower end surface of downward through described eccentric part, the simultaneously outer circumferential face of described first loss of weight equalizing orifice also through described eccentric part.
2. bent axle according to claim 1, is characterized in that, the outer circumferential face of described main shaft part is provided with multiple protruding structure, and two adjacent described protruding structures limit a described first loss of weight equalizing orifice.
3. bent axle according to claim 2, is characterized in that, is provided with the second loss of weight equalizing orifice in protruding structure described at least one.
4. bent axle according to claim 3, is characterized in that, the through hole that described second loss of weight equalizing orifice is eccentric part described in up/down perforation.
5. bent axle according to claim 4, it is characterized in that, also comprise: horizontal baffle, described horizontal baffle is orthogonal to the central axis of described main shaft part and is arranged in described second loss of weight equalizing orifice, and the inner peripheral surface of the outer circumferential face of described horizontal baffle and described second loss of weight equalizing orifice is fitted in the circumferential at least in part.
6. bent axle according to claim 5, is characterized in that, the hole structure that the inner bottom part that described horizontal baffle is arranged on described second loss of weight equalizing orifice opens wide to make described second loss of weight equalizing orifice be configured to top; Or
The inner top that described horizontal baffle is arranged on described second loss of weight equalizing orifice is configured to the hole structure of bottom-open to make described second loss of weight equalizing orifice; Or
Described horizontal baffle respectively with the upper-end surface of described eccentric part and lower end surface spaced apart.
7. bent axle according to claim 1, is characterized in that, the outer circumferential face of described main shaft part is provided with multiple connecting plate, and the free end of each described connecting plate is provided with arc plate, and two adjacent connecting plates limit a described first loss of weight equalizing orifice.
8. bent axle according to claim 1, it is characterized in that, described first loss of weight equalizing orifice is positioned at the side of the central axis towards described eccentric part of the first longitudinal plane, and described first longitudinal plane is central axis by described main shaft part and is orthogonal to the plane of the line of centres of described main shaft part and described eccentric part.
9. bent axle according to claim 8, is characterized in that, described first loss of weight equalizing orifice is divided into two groups, and described two group of first loss of weight equalizing orifice is symmetrical about the second longitudinal plane of the line of centres by described main shaft part and described eccentric part.
10. a rotary compressor, is characterized in that, comprises the bent axle according to any one of claim 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520479558.2U CN204783676U (en) | 2015-07-02 | 2015-07-02 | Rotary compressor and bent axle thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520479558.2U CN204783676U (en) | 2015-07-02 | 2015-07-02 | Rotary compressor and bent axle thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204783676U true CN204783676U (en) | 2015-11-18 |
Family
ID=54523734
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520479558.2U Expired - Fee Related CN204783676U (en) | 2015-07-02 | 2015-07-02 | Rotary compressor and bent axle thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204783676U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104963867A (en) * | 2015-07-02 | 2015-10-07 | 广东美芝制冷设备有限公司 | Rotary compressor and crankshaft thereof |
-
2015
- 2015-07-02 CN CN201520479558.2U patent/CN204783676U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104963867A (en) * | 2015-07-02 | 2015-10-07 | 广东美芝制冷设备有限公司 | Rotary compressor and crankshaft thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104963868A (en) | Rotary compressor and crankshaft thereof | |
| US20120189470A1 (en) | Compressor | |
| CN104612974A (en) | Rotary compressor | |
| JP2014196714A (en) | Multicylinder rotary compressor | |
| CN204783676U (en) | Rotary compressor and bent axle thereof | |
| CN204003477U (en) | Horizontal compressor | |
| CN205036580U (en) | Multi -cylinder rotary compressor | |
| CN105221424A (en) | Rotary compressor and there is its heat pump | |
| CN204783677U (en) | Rotary compressor and bent axle thereof | |
| CN104963867A (en) | Rotary compressor and crankshaft thereof | |
| CN204729305U (en) | The piston of rotary compressor and there is its rotary compressor, multistage compressor | |
| CN204312332U (en) | Compressor | |
| CN204900259U (en) | Rotary compressor and bent axle thereof | |
| CN105201845A (en) | Rotary compressor | |
| CN105003526A (en) | Rotary compressor and crankshaft thereof | |
| CN203717352U (en) | Compressing pump body of rotary compressor | |
| CN202520559U (en) | Crankshaft structure of rolling rotor compressor | |
| CN204941942U (en) | Rotary compressor and compression assembly thereof | |
| CN204436740U (en) | Compressor | |
| CN103410736A (en) | Low-backpressure rotary compressor and refrigeration equipment adopting same | |
| CN204061094U (en) | Duplex cylinder compressor and the air-conditioning with it | |
| CN205172951U (en) | A motor element and rotary compressor for compressor | |
| CN202326240U (en) | Closed type compressor and refrigeration circulating device | |
| CN104653459A (en) | Compressor | |
| CN204371682U (en) | Rotary compressor and there is its refrigeration plant |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20151118 Termination date: 20200702 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |