CN204371671U - Rotary compressor - Google Patents

Abstract

The utility model discloses a kind of rotary compressor, comprise: housing, cylinder, piston and slide plate, in housing, there is refrigerator oil, cylinder is located in housing, there is in cylinder the compression chamber for compression refrigerant, cylinder is formed with the radial vane slot extended, vane slot is communicated with compression chamber, piston is located in compression chamber and inwall along compression chamber can roll, slide plate is located in vane slot movably by spring, and the periphery wall of the inner of slide plate and piston only supports, when distance wherein between piston and vane slot is maximum, spring meets the spring force F of slide plate: 3N≤F≤20N.According to rotary compressor of the present utility model, by limiting spring to the value of the minimum spring force of slide plate, thus effectively can improve slide plate mail topic, and can indirectly control spring to the value of the maximum spring force of slide plate, and then reduce the power consumpiton of rotary compressor, improve the overall efficiency of rotary compressor.

Description

Rotary compressor

Technical field

The utility model relates to compressor apparatus field, especially relates to a kind of rotary compressor.

Background technique

Point out in correlation technique, in compressor operating process, usually there is different mail topic in slide plate, concrete analysis, power suffered by slide plate is making a concerted effort of spring force, gas force and frictional force, wherein, the size of the influence of specification spring force of spring, when spring force is too small, the followability of slide plate declines, cause slide plate sound serious, and when spring force is excessive, fatigue fracture easily occurs spring, the frictional force acted between piston external diameter and slide plate the inner is larger, the power of compressor is higher, efficiency is lower, and therefore spring force is unsuitable excessive or too small; In compressor, the lubrication circumstances of refrigerator oil affects the size of frictional force, when the dissolving viscosity of refrigerator oil is too low, slide plate lubricating status is poor, frictional force is comparatively large, and the followability of slide plate is poor, and slide plate sound is serious, and the efficiency of compressor also can decline, when the dissolving viscosity of refrigerator oil is excessive, the viscosity factor of slide plate is comparatively large, resistance is higher, and slide plate followability is also poor, compressor efficiency also can decline, and therefore the dissolving viscosity of refrigerator oil is unsuitable excessive or too small.

Model utility content

The utility model is intended at least to solve one of technical problem existed in prior art.For this reason, the utility model is to propose a kind of rotary compressor, and described rotary compressor can improve slide plate sound, improves efficiency.

According to rotary compressor of the present utility model, comprising: housing, in described housing, there is refrigerator oil; Cylinder, described cylinder is located in described housing, has the compression chamber for compression refrigerant in described cylinder, and described cylinder is formed with the radial vane slot extended, described vane slot is communicated with described compression chamber; Piston, described piston is located in described compression chamber and inwall along described compression chamber can roll; And slide plate, described slide plate is located in described vane slot by spring movably, and the periphery wall of the inner of described slide plate and described piston only supports, when the distance wherein between described piston and described vane slot is maximum, described spring meets the spring force F of described slide plate: 3N≤F≤20N.

According to rotary compressor of the present utility model, by limiting spring to the value of the minimum spring force of slide plate, thus effectively can improve slide plate mail topic, and can indirectly control spring to the value of the maximum spring force of slide plate, and then reduce the power consumpiton of rotary compressor, improve the overall efficiency of rotary compressor.

Particularly, when the quality m of described slide plate meets: during m≤20g, described F meets: 3N≤F≤10N; When the quality m of described slide plate meets: during 20g<m≤35g, described F meets: 7N≤F≤13N; When the quality m of described slide plate meets: during 35g<m≤50g, described F meets: 10N≤F≤15N; When the quality m of described slide plate meets: during m > 50g, described F meets: 10N≤F≤20N.

Alternatively, described spring is multiple, and described spring force F is described multiple spring making a concerted effort to described slide plate.

Particularly, described multiple spring is arranged in parallel.

Particularly, described refrigerant is R22 or R290, when the exhaust pressure P of described rotary compressor meets: 1.0MPa≤P≤2.0MPa and the temperature T of described refrigerator oil meet: during 50 DEG C≤T≤85 DEG C, the dissolving viscosity, mu of described refrigerator oil meets: 1.0cP≤μ≤5.0cP.

Particularly, described refrigerant is R410A, when the exhaust pressure P of described rotary compressor meets: 1.5MPa≤P≤3.5MPa and the temperature T of described refrigerator oil meet: during 50 DEG C≤T≤85 DEG C, the dissolving viscosity, mu of described refrigerator oil meets: 1.5cP≤μ≤6.0cP.

Alternatively, described refrigerator oil is mineral oil and/or artificial oil.

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.

Accompanying drawing explanation

Fig. 1 is the part sectioned view of the rotary compressor according to the utility model embodiment;

Fig. 2 is the schematic diagram of the cylinder shown in Fig. 1, slide plate, spring and piston;

Fig. 3 is the schematic diagram of relation between minimum spring force and slide plate sound grade;

Fig. 4 is the schematic diagram of relation between maximum spring force and crank torque;

Fig. 5 is the schematic diagram of relation between maximum spring force and rotary compressor COP;

Fig. 6 is the schematic diagram that refrigerator oil dissolves relation between viscosity and compressor COP;

Fig. 7 is the schematic diagram that refrigerator oil dissolves relation between viscosity and slide plate sound grade.

Reference character:

100: rotary compressor;

1: housing; 11: middle casing; 12: lower shell body;

2: electric machine assembly; 21: stator; 22: rotor; 3: bent axle;

4: compressing mechanism; 41: cylinder; 42: piston; 43: main bearing; 44: supplementary bearing;

45: slide plate; 46: spring.

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.

Disclosing hereafter provides many different embodiments or example is used for realizing different structure of the present utility model.Of the present utility model open in order to simplify, hereinafter the parts of specific examples and setting are described.Certainly, they are only example, and object does not lie in restriction the utility model.In addition, the utility model can in different example repeat reference numerals and/or letter.This repetition is to simplify and clearly object, itself does not indicate the relation between discussed various embodiment and/or setting.In addition, the various specific technique that the utility model provides and the example of material, but those of ordinary skill in the art can recognize the property of can be applicable to of other techniques and/or the use of other materials.

Below with reference to Fig. 1-Fig. 7, the rotary compressor 100 according to the utility model embodiment is described.Wherein, rotary compressor 100 can be the adjustable frequency-changeable compressor of rotating speed, also can be the certain constant speed compressor of rotating speed.In addition, it should be noted that, rotary compressor 100 can be vertical compressor, can be also horizontal compressor, only be described for vertical compressor for rotary compressor 100 below.

As shown in Figure 1, according to the rotary compressor 100 of the utility model embodiment, comprising: housing 1, electric machine assembly 2, bent axle 3 and compressing mechanism 4.

Particularly, as shown in Figure 1, housing 1 can comprise upper shell (scheming not shown), middle casing 11 and lower shell body 12, upper shell and lower shell body 12 are connected to top and the bottom of middle casing 11, seal and the cylindrical shell 1 of hollow jointly to limit with middle casing 11, preferably, middle casing 11 can adopt welding procedure to be integrally fixed structure respectively with upper shell and lower shell body 12.Certainly, be understandable that, the structure of housing 1 is not limited thereto.

Further, as shown in Figure 1, electric machine assembly 2 can be located at the top in housing 1, compressing mechanism 4 can be located in housing 1 and to be positioned at the below of electric machine assembly 2, wherein, electric machine assembly 2 can comprise stator 21 and rotor 22, stator 21 can be fixed together with the periphery wall of middle casing 11, rotor 22 can be located in stator 21 rotationally, the upper end of bent axle 3 can be fixed together with rotor 22 hot jacket, thus rotor 22 can driving crank 3 flexing axle 3 central axis rotate, compressing mechanism 4 is run through in the bottom of bent axle 3, thus can refrigerant in compression compressors structure 4 in bent axle 3 process of rotating.

Particularly, as depicted in figs. 1 and 2, compressing mechanism 4 can comprise: cylinder assembly, piston 42, slide plate 45 and main bearing 43 and supplementary bearing 44.Wherein, when rotary compressor 100 is single cylinder rotary compressor, cylinder assembly only comprises a cylinder 41, when rotary compressor 100 is multi-cylinder rotary compressor, cylinder assembly is included in multiple cylinders 41 that above-below direction is arranged, and is provided with dividing plate between two often adjacent cylinders 41.Only be described for single cylinder rotary compressor for rotary compressor 100 below.

There is in cylinder 41 compression chamber for compression refrigerant.As shown in Figure 1, cylinder 41 is formed with the opening run through along cylinder 41 thickness direction, main bearing 43 can be fixed on the top on cylinder 41 thickness direction, supplementary bearing 44 can be fixed on the bottom on cylinder 41 thickness direction, thus main bearing 43 and supplementary bearing 44 can limit compression chamber jointly with the opening of cylinder 41, among main bearing 43, supplementary bearing 44, cylinder 41, the periphery wall of at least one can the inner circle wall of middle casing 11 be fixed together by the mode of spot welding, and the lower end of bent axle 3 runs through main bearing 43, cylinder 41 and supplementary bearing 44 in turn.

Further, as depicted in figs. 1 and 2, piston 42 is located in compression chamber, and piston 42 can roll along the inwall of compression chamber.Wherein, the bottom of bent axle 3 has eccentric part, wherein eccentric part is arranged in compression chamber, piston 42 is constructed generally as ring, and is set on eccentric part, when in the process that rotor 22 driving crank 3 rotates, bent axle 3 can drive eccentric part and piston 42 together to rotate, thus piston 42 can be rolled along the inwall of compression chamber, when in the process that piston 42 rolls, the periphery wall of piston 42 linearly abuts with the inner circumferential sidewall of compression chamber all the time.

Again further, as depicted in figs. 1 and 2, cylinder 41 is formed with the radial vane slot extended, slide plate 45 is located in vane slot movably, and the periphery wall of the inner of slide plate 45 and piston 42 only supports.Wherein, the cross section of vane slot is constructed generally as rectangle, and vane slot can be formed towards away from the direction at compression chamber center is recessed by the inwall of compression chamber, thus vane slot is connected with compression chamber.Here, it should be noted that, " interior " can be understood as the direction towards cylinder 41 central axis, and its opposite direction is defined as " outward ", namely away from the direction of cylinder 41 central axis.

With reference to Fig. 2, slide plate 45 is located in vane slot slidably by spring 46, one end away from cylinder 41 center of its medi-spring 46 is connected with cylinder 41, the one end at contiguous cylinder 41 center of spring 46 is connected with the outer end of slide plate 45, wherein, spring 46 is in compressive state all the time, thus the inner that can promote slide plate 45 under the effect of the elastic force of spring 46 to extend in compression chamber and is only against on the periphery wall of piston 42, like this, in the process that bent axle 3 driven plunger 42 is rolled, slide plate 45 can do back and forth to retreat and move under piston 42 with the double action of spring 46 in vane slot.

In the process that slide plate 45 moves, because the outer end of slide plate 45 is positioned at vane slot all the time, and the inner of slide plate 45 closely abuts with the periphery wall of piston 42 all the time, thus compression chamber can be separated into the air aspiration cavity and exhaust cavity that are isolated from each other by slide plate 45 and piston 42, roll at piston 42, slide plate 45 slide process in, the spatial volume of air aspiration cavity and exhaust cavity constantly changes, to realize the compression of refrigerant.

Particularly, suffered in the reciprocating process of slide plate 45 power comprises: the contact friction of the spring force that the gas force that the pressure reduction between the air pressure of slide plate 45 outer end and the air pressure of slide plate 45 the inner produces, the spring 46 being arranged on slide plate 45 outer end produce, slide plate 45 and vane slot, main bearing 43, supplementary bearing 44 and the frictional force that produces.

For ensureing not depart from piston 42 in the process that slide plate 45 moves, must ensure that the speed of any moment slide plate 45 motion is all greater than the speed of piston 42 motion, and in the reciprocating process of slide plate 45, slide plate 45 and piston 42 are when top dead center, bottom dead center position, speed is 0, if ensure that the speed of slide plate 45 is greater than the speed of piston 42, then must ensure that the acceleration of slide plate 45 is greater than the acceleration of piston 42.Here, it should be noted that, " lower dead center " refers to piston 42 and vane slot distance position (as shown in Figure 2) farthest, and " top dead center " refers to piston 42 position nearest with vane slot.

As mentioned above, spring force Fk, gas force Fp, frictional force Fc three make a concerted effort Fh must be greater than piston 42 run inertial force Fm, i.e. Fk+Fp+Fc>-Fm, wherein, the direction of frictional force Fc changes according to the change of slide plate 45 moving direction, when the traffic direction of slide plate 45 is identical with the direction of spring force, Fc is negative, when the traffic direction of slide plate 45 is contrary with the direction of spring force, Fc is just, the direction of inertial force Fm is contrary with the direction of acceleration, when the direction of acceleration is identical with the direction of spring force, Fm is negative, when the direction of acceleration is contrary with the direction of spring force, Fm is just.

As shown in Figure 2, slide plate 45 is stressed as shown in mark in figure, when slide plate 45 runs to the below shown in figure, spring force Fk suffered by slide plate 45 is downward, gas force Fp is downward, frictional force Fc upwards, then make a concerted effort Fh=Fk+Fp-Fc, now, Fh must ensure to be greater than inertial force Fm, i.e. Fk+Fp-Fc>-Fm, and Fm=m × a1, wherein, m is the weight of slide plate 45, a1 is the acceleration of piston 42, acceleration a2 due to slide plate 45 must be greater than the acceleration a1 of piston 42, thus when slide plate 45 moves to top dead center, the length of spring 46 is the shortest, spring force is maximum, for Fk1, now slide plate 45 speed is 0, but now the acceleration of slide plate 45 is maximum, for a21, and the acceleration direction of slide plate 45 is identical with the direction of inertial force, when slide plate 45 moves to lower dead center, the length of spring 46 is the longest, spring force is minimum, for Fk2, now slide plate 45 speed is similarly 0, but now the acceleration of slide plate 45 is that a22 is less than a21, and it is contrary with the direction of a21.

Particularly, the change in displacement of piston 42 is certain rule, and acceleration also carries out circulation change within a cycle.So, in order to ensure that slide plate 45 closely followed by piston 42, do not depart from piston 42, then must ensure that the acceleration a2 of any moment slide plate 45 is greater than the acceleration a1 of piston 42, the situation only moving to top dead center position and bottom dead center position for piston 42 and slide plate 45 below illustrates.

When slide plate 45 is at top dead center position, ensure that the speed of slide plate 45 is greater than the speed of piston 42, because slide plate 45 and piston 42 speed are 0, then need to ensure that the acceleration a21 of slide plate 45 is greater than piston 42 acceleration a1, so in gas force Fp and frictional force Fc mono-timing, must ensure that spring force Fk1 is greater than certain certain value, guarantee is made a concerted effort enough large, to ensure that acceleration a21 is enough large.

When slide plate 45 runs to bottom dead center position, acceleration a22 due to slide plate 45 is contrary with the speed of slide plate 45 is negative value, the Fm2 that makes a concerted effort of frictional force Fc, gas force Fp, spring force Fk2 is for negative, sufficiently little, the acceleration a22 of guarantee slide plate 45 is less than piston 42 acceleration a1, that is, when only having the velocity attenuation when slide plate 45 to be less than the velocity attenuation of piston 42, guarantee slide plate 45 does not depart from piston 42, so now spring force Fk2 needs enough large, guarantee its make a concerted effort less, the speed of guarantee slide plate 45 is greater than the speed of piston 42.

In sum, run at rotary compressor 100, in the slide plate 45 reciprocal cycle run, must ensure that spring force is enough large, could produce by anti-slip limiting plate sound, and when spring force is excessive, can impact again the power consumption of rotary compressor 100, therefore the size of spring force need ensure in certain scope, guarantee slide plate 45 does not depart from piston 42, to improve slide plate mail topic, avoids the problem that the power consumption of rotary compressor 100 increases, efficiency declines simultaneously.

In brief, between spring force and slide plate sound, efficiency, there is close relationship, spring force not only affects the slide plate timbre matter of rotary compressor 100 but also affects the efficiency of rotary compressor 100, thus only have spring force in certain interval, slide plate sound and COP (abbreviation of coefficient of performance, Energy Efficiency Ratio) could have good performance simultaneously.

Experimental result is as shown in Fig. 3 and following table, when the minimum spring force Fk2 of spring 46 changes, slide plate sound also can be under some influence, particularly, when the weight of slide plate 45 is constant, when Fk2 value is less than certain certain value, slide plate sound can produce, and Fk2 is less, slide plate sound is more obvious, and weaken along with the increase slide plate sound of minimum spring force Fk2, when Fk2 is greater than certain certain value, in compressor, there is not slide plate sound.

Here, it should be noted that, A4>A3>A2>A1 in upper table, B4>B3>B2>B1, and be the grade of artificial definition with the slide plate sound grade shown in Fig. 3 in upper table, only do and explain explanation use, can not be interpreted as restriction of the present utility model.

But, by the impact of spring 46 structure and design, minimum spring force Fk2 can not infinitely increase, because during increase along with minimum spring force Fk2, maximum spring force Fk1 also can increase to some extent, as shown in Figure 4, the increase of maximum spring force Fk1, the rotation torque of bent axle 3 can be made to increase, and namely illustrate that rotor 22 rotates the resistance that will overcome and increases, the power that rotary compressor 100 consumes increases, efficiency declines.In addition, the design of increase on spring 46 of spring force causes very large impact, such as, the stress of spring 46 can be caused to increase, make spring 46 easily occur the problem of fatigue failure.

In addition, obvious relation is also had between spring force and the efficiency of compressor.Such as in the example of hgure 5, when spring 46 is under a certain quality, when Fk1 is less than certain certain value, the followability of slide plate 45 is poor, slide plate 45 and piston 42 depart from, thus cause the refrigerant in compression chamber to leak to air aspiration cavity, cause loss of refrigeration capacity, COP is caused to decline, also can produce slide plate sound simultaneously, and when spring force Fk1 more hour, slide plate 45 departs from more serious, cold leaks larger, COP is less, and when spring force Fk1 is greater than certain certain value, slide plate 45 followability is good, there is not slide plate 45 break-off, compressor cold does not leak, COP is improved, but when spring force Fk1 continues to increase, produce frictional loss in slide plate 45 and piston 42 movement process to strengthen, compressor horsepower increases, COP will be caused again to decline, thus draw, when maximum spring force Fk1 meets: 15≤Fk1≤35N, rotary compressor 100 has good efficiency performance.

In sum, when the distance between piston 42 and vane slot is maximum, the spring force F of spring 46 pairs of slide plates 45 meets: 3N≤F≤20N, and that is, when piston 42 moves to bottom dead center position, the minimum spring force Fk2 of spring 46 meets: 3N≤Fk2≤20N.Thus, not only can improve slide plate mail topic, and the maximum spring force Fk1 of slide plate 45 can be avoided excessive, thus avoid the impact on bent axle 3 rotation torque, and effectively can ensure that rotary compressor 100 has excellent efficiency performance.

According to the rotary compressor 100 of the utility model embodiment, by limiting the value of the minimum spring force of spring 46, thus effectively can improve slide plate mail topic, and the maximum spring force of slide plate 45 can be avoided excessive, and then the impact avoiding bent axle 3 rotation torque, and effectively can ensure that rotary compressor 100 has excellent efficiency performance.

Experiment shows, when the weight of slide plate 45 changes, the overall performance of spring 46 changes, thus in order to meet rotary compressor 100 without slide plate sound, and in order to ensure the efficiency of rotary compressor 100, need the span of the minimum spring force specifically determining spring 46.

Particularly, when the quality m of slide plate 45 meets: during m≤20g, F meets: 3N≤F≤10N, that is, the minimum spring force Fk2 of spring 46 meets: 3N≤Fk2≤10N.

When the quality m of slide plate 45 meets: during 20g<m≤35g, F meets: 7N≤F≤13N, that is, the minimum spring force Fk2 of spring 46 meets: 7N≤Fk2≤13N.

When the quality m of slide plate 45 meets: during 35g<m≤50g, F meets: 10N≤F≤15N, that is, the minimum spring force Fk2 of spring 46 meets: 10N≤Fk2≤15N.

When the quality m of slide plate 45 meets: during m > 50g, F meets: 10N≤F≤20N, that is, the minimum spring force Fk2 of spring 46 meets: 10N≤Fk2≤20N.

In an embodiment of the present utility model, when spring force one timing, and when the operating conditions of rotary compressor 100 and range of operation are determined, if the frictional force Fc of slide plate 45 operation can be reduced, then can ensure the followability of slide plate 45 equally, effectively to improve slide plate mail topic.Thus, according to above-mentioned principle, when slide plate 45 frictional force Fc more hour, acceleration, the speed of slide plate 45 are more guaranteed.

Particularly, have refrigerator oil in housing 1, refrigerator oil can be the miscella of mineral oil, artificial oil or mineral oil and artificial oil, such as POE, PVE, PAG or AB wet goods.

The frictional force Fc of slide plate 45 and refrigerator oil dissolve viscosity and there are much relations, when refrigerator oil dissolving viscosity is too small, oil film forms difficulty, thus causing slide plate 45 to run close to dry friction, friction factor is increased, and frictional force increases, when refrigerator oil dissolving viscosity is excessive, the viscosity factor of refrigerator oil increases, and frictional force also can increase, thus the followability tool of the dissolving viscosity of refrigerator oil to slide plate 45 has a great impact.

Such as in the example in figure 7, illustrate the relation that refrigerator oil dissolves viscosity and slide plate sound, as can be seen from the figure, when dissolving viscosity and being less than a certain value, along with the dissolving viscosity of refrigerator oil increases, slide plate sound can improve, when dissolving viscosity and being greater than a certain value, along with the increase of the dissolving viscosity of refrigerator oil, the viscous resistance of refrigerator oil increases, and corruptions appears in slide plate sound.

Thus, under the operating mode that compressor efficiency is evaluated, when the dissolving viscosity of refrigerator oil changes, also can there is corresponding change in compressor efficiency, as shown in Figure 6, is dissolving viscosity and the compressor energy effect relationship of refrigerator oil.Particularly, when refrigerator oil dissolving viscosity is too small, refrigerator oil oil film forms difficulty, lubricating status between slide plate 45 and other kinematic pair is severe, friction factor increases, compressor mechanical consumption increases, COP declines, resistance to motion simultaneously because of slide plate 45 increases, the followability of slide plate 45 also can be affected, when refrigerator oil dissolving viscosity is less than certain certain value, slide plate sound produces, compressor cold is caused to decline, compressor COP declines, when refrigerator oil dissolves viscosity increase, lubricate between slide plate 45 and other kinematic pair and improve, slide plate sound disappears, resistance to motion simultaneously between kinematic pair declines, compressor cold rises, power drop, COP increases, when refrigerator oil dissolving viscosity increases further, oil product strengthens the viscous resistance between kinematic pair, motion power consumption is caused to increase, slide plate 45 followability is poor, compressor COP is caused to decline.

Preferably, when refrigerant is the less refrigerant of the saturation pressures such as R22 or R290, when the exhaust pressure P of rotary compressor 100 meets: 1.0MPa≤P≤2.0MPa and the temperature T of refrigerator oil (oil sump namely in housing 1) are satisfied: during 50 DEG C≤T≤85 DEG C, the dissolving viscosity, mu of refrigerator oil meets: 1.0cP≤μ≤5.0cP, now, the slide plate sound of rotary compressor 100 and efficiency performance are better.

Preferably, when refrigerant is the larger refrigerant of the saturation pressures such as R410A, when the exhaust pressure P of rotary compressor 100 meets: 1.5MPa≤P≤3.5MPa and the temperature T of refrigerator oil (oil sump namely in housing 1) are satisfied: during 50 DEG C≤T≤85 DEG C, the dissolving viscosity, mu of refrigerator oil meets: 1.5cP≤μ≤6.0cP, now, the slide plate sound of rotary compressor 100 and efficiency performance are better.Here, it should be noted that, refrigerant can be combustible refrigerant, can also be non-combustible refrigerant.

In sum, by appropriate design spring 46 and select suitable refrigerator oil, the followability of slide plate 45 and the efficiency of rotary compressor 100 can be ensured, specifically, all be in proper scope by the dissolving range of viscosities of the spring force scope and refrigerator oil of guaranteeing spring 46, to ensure that slide plate 45 has followability well, thus make the efficiency of rotary compressor 100 also be guaranteed and improve, ensure that noise quality and the efficiency of rotary compressor 100.

Rotary compressor 100 according to the utility model embodiment is comparatively applicable to the low frequency conversion machine of rotating speed, and is comparatively applicable to running the compressor that in the lower refrigerant of minimum pressure reduction and range of operation, pressure reduction is lower.

Alternatively, spring 46 is multiple, and spring force F is making a concerted effort of multiple springs 46 pairs of slide plates 45.Preferably, multiple spring 46 is arranged in parallel.That is, the outer end of each spring 46 is all connected with cylinder 41, and the inner of each spring 46 is all connected with the outer end of slide plate 45, and the compression direction of each spring 46 is identical.

Here, it should be noted that, the numeral shown in Fig. 3-Fig. 7 only illustrates for illustrating, therefore 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 ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " 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 the utility model, 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 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, the concrete meaning of above-mentioned term in the utility model can be understood as the case may be.

In the utility model, 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 utility model 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 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 (7)

1. a rotary compressor, is characterized in that, comprising:

Housing, has refrigerator oil in described housing;

Cylinder, described cylinder is located in described housing, has the compression chamber for compression refrigerant in described cylinder, and described cylinder is formed with the radial vane slot extended, described vane slot is communicated with described compression chamber;

Piston, described piston is located in described compression chamber and inwall along described compression chamber can roll; And

Slide plate, described slide plate is located in described vane slot by spring movably, and the periphery wall of the inner of described slide plate and described piston only supports, when the distance wherein between described piston and described vane slot is maximum, described spring meets the spring force F of described slide plate: 3N≤F≤20N.

2. rotary compressor according to claim 1, is characterized in that,

When the quality m of described slide plate meets: during m≤20g, described F meets: 3N≤F≤10N;

When the quality m of described slide plate meets: during 20g<m≤35g, described F meets: 7N≤F≤13N;

When the quality m of described slide plate meets: during 35g<m≤50g, described F meets: 10N≤F≤15N;

When the quality m of described slide plate meets: during m > 50g, described F meets: 10N≤F≤20N.

3. rotary compressor according to claim 1, is characterized in that, described spring is multiple, and described spring force F is described multiple spring making a concerted effort to described slide plate.

4. rotary compressor according to claim 3, is characterized in that, described multiple spring is arranged in parallel.

5. rotary compressor according to claim 1, it is characterized in that, described refrigerant is R22 or R290, when the exhaust pressure P of described rotary compressor meets: 1.0MPa≤P≤2.0MPa and the temperature T of described refrigerator oil meet: during 50 DEG C≤T≤85 DEG C, the dissolving viscosity, mu of described refrigerator oil meets: 1.0cP≤μ≤5.0cP.

6. rotary compressor according to claim 1, it is characterized in that, described refrigerant is R410A, when the exhaust pressure P of described rotary compressor meets: 1.5MPa≤P≤3.5MPa and the temperature T of described refrigerator oil meet: during 50 DEG C≤T≤85 DEG C, the dissolving viscosity, mu of described refrigerator oil meets: 1.5cP≤μ≤6.0cP.

7. the rotary compressor according to any one of claim 1-6, is characterized in that, described refrigerator oil is mineral oil and/or artificial oil.