CN107120275B

CN107120275B - Compression mechanism and rotary compressor

Info

Publication number: CN107120275B
Application number: CN201710515560.4A
Authority: CN
Inventors: 谭琴; 宋鹏杰
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2017-06-29
Filing date: 2017-06-29
Publication date: 2021-05-28
Anticipated expiration: 2037-06-29
Also published as: CN107120275A

Abstract

The invention provides a compression mechanism and a rotary compressor, wherein the compression mechanism comprises: the cylinder assembly comprises at least one cylinder, and an eccentric rotary piston is correspondingly arranged in a cavity of each cylinder; at least one supporting component, with every cylinder subassembly cooperation setting to the closed cavity, wherein, the inside wall of cavity, eccentric rotary piston 'S lateral wall and supporting component' S closed surface enclose to close and form at least one working chamber, and at least one exhaust hole has been seted up to every working chamber, and the sum V of the volume of all working chambers, and the sum S of the cross sectional area of all exhaust holes satisfy: V/S is more than or equal to 60mm and less than or equal to 140 mm. Through the technical scheme of the invention, on one hand, the exhaust resistance loss of the compression mechanism can be reduced, on the other hand, the operation efficiency of the compression mechanism can be improved, and the noise generated in the operation process of the compression mechanism can be reduced.

Description

Compression mechanism and rotary compressor

Technical Field

The invention relates to the field of compressors, in particular to a compression mechanism and a rotary compressor.

Background

In the related art, the rotary compressor is increasingly miniaturized and high-speed, the rated rotation speed is increased from 60rps to 90rps or more, and the maximum rotation speed is increased from 120rps to 180rps or more. The higher the speed, the more gas is discharged per unit time and the higher the exhaust flow rate. Since the exhaust resistance loss is quadratically related to the exhaust flow rate, the proportion of the exhaust resistance loss to the total energy consumption increases sharply with increasing rotational speed, resulting in a decrease in the compressor energy efficiency. But also an increase in airflow noise due to the increase in exhaust flow velocity.

Increasing the discharge cross-sectional area is an effective way to reduce the discharge resistance loss of the compressor, however, the increase of the discharge cross-sectional area will result in an increase of the clearance volume and a decrease of the volumetric efficiency, resulting in an influence on the working performance of the compressor.

Disclosure of Invention

In order to solve at least one of the above-mentioned technical problems, it is an object of the present invention to provide a compression mechanism.

Another object of the present invention is to provide a rotary compressor.

In order to achieve the above object, an embodiment of a first aspect of the present invention proposes a compression mechanism including: the cylinder assembly comprises at least one cylinder, and an eccentric rotary piston is correspondingly arranged in a cavity of each cylinder; at least one supporting component, with every cylinder subassembly cooperation setting to the closed cavity, wherein, the inside wall of cavity, eccentric rotary piston 'S lateral wall and supporting component' S closed surface enclose to close and form at least one working chamber, and at least one exhaust hole has been seted up to every working chamber, and the sum V of the volume of all working chambers, and the sum S of the cross sectional area of all exhaust holes satisfy:

in the technical scheme, the ratio of the sum of the volumes of all the working chambers to the sum of the cross-sectional areas of all the exhaust holes is limited within a specified numerical range, so that when the rotating speed of the compression mechanism is in high-speed rotation (greater than or equal to 90rps), on one hand, the exhaust resistance loss of the compression mechanism can be reduced, on the other hand, the operation efficiency of the compression mechanism can be improved, and the noise generated in the operation process of the compression mechanism can be reduced.

The motor of the rotary compressor does not need to convert the rotary motion of the rotor into the reciprocating motion of the piston, but directly drives the rotary piston to rotate to complete the compression of the refrigerant vapor.

The structure of rotary compressor is mainly characterized by that it uses eccentric rotor to act as piston to compress refrigerant gas, and the rotating crankshaft is coaxial with cylinder shaft, and on the rotating crankshaft an eccentric wheel is mounted, and on the eccentric wheel a thin-wall elastic sleeve rotor supported by high-quality steel is mounted so as to form an eccentric rotating piston, one side of the eccentric rotating piston is always tightly contacted with inner side wall of cylinder, and between the outer surface of the eccentric rotating piston and inner side wall of cylinder a crescent working cavity is formed.

Specifically, when the rated rotation speed of the rotary compressor is greater than or equal to 90rps, V/S is greater than or equal to 60mm and less than or equal to 140mm, wherein V is the sum of the volumes of all working cavities, and S is the sum of the cross-sectional areas of all exhaust holes.

In order to keep the range of the average Mach number M of the exhaust gas constant when the rated rotation speed is increased to 90rps, the range of V/S is changed to 120mm < V/S < 200mm, and the value of V/S is further decreased in consideration of the fact that the higher the rotation speed is, the greater the adverse effect of the exhaust gas interruption on the exhaust gas is, and in consideration of the case that the rated rotation speed is greater than 90rps, assuming that the volume of three working chambers (9.8 x 10)³mm³，22×10³mm³，48×10³mm³) And then, three-dimensional fluid-solid coupling simulation calculation is carried out at three corresponding rotating speeds (90rps/120rps/150rps), and the result shows that when the V/S range is 60 mm-140 mm, the performance of the rotary compressor is higher.

The section of the exhaust hole can be round, long round, polygonal and the like.

In addition, the compression mechanism in the above embodiment provided by the present invention may further have the following additional technical features:

in the above technical solution, preferably, the support assembly includes: the first bearing and the second bearing are respectively attached to two outer side end faces of the air cylinder assembly, the outer side end faces are provided with axial openings of the working cavities, regions of the first bearing corresponding to the axial openings form first closed faces, regions of the second bearing corresponding to the axial openings form second closed faces, and exhaust holes are formed in the first closed faces and/or the second closed faces.

In this technical scheme, through setting up the supporting component to including first bearing and second bearing, when setting up to single cylinder promptly, set up first bearing and second bearing respectively at the both ends of single cylinder, the first bearing forms first closed surface with the region that the axial opening corresponds, and the second bearing forms the second closed surface with the region that the axial opening corresponds, through seting up the exhaust hole on first closed surface and/or second closed surface, has realized the discharge of single cylinder compressor's compressed gas.

The compression mechanism comprises a main bearing, a secondary bearing, a plurality of exhaust holes and a compression mechanism, wherein the first bearing is the main bearing, the second bearing is the secondary bearing, only one exhaust hole can be arranged on the main bearing, the exhaust holes can also be arranged on the first bearing and the second bearing respectively, and the compression mechanism can be accelerated by increasing the area of the exhaust holes on the premise that V/S is not less than 60mm and not more than 140 mm.

Specifically, considering the eccentric amount of the eccentric rotary piston and the utilization rate of the exhaust area, the sectional area of a single exhaust hole cannot be designed to be too large, and often, two or more exhaust holes are formed in one working cavity, and the sectional areas of the exhaust holes may be equal or unequal.

For example, in the case of a single cylinder compression mechanism, two exhaust holes having the same diameter are opened in the working chamber, and when the exhaust holes are circular holes, the volume V of the working chamber of the compressor is 10.555 × 10³(mm³) When the diameter of the vent hole is larger than or equal to 4.90 multiplied by 10^-3m, and less than or equal to 7.48X 10^-3m。

In any one of the above technical solutions, preferably, the number of the cylinders is greater than or equal to 2, and the plurality of cylinders are arranged side by side in sequence along the axial direction, and the support assembly further includes: the first partition plate is attached to the position between any two adjacent cylinders, an axial opening is formed in the attaching surface of any two adjacent cylinders and the first partition plate, a third sealing surface and a fourth sealing surface are formed in the regions, corresponding to the axial opening, of the two sides of the first partition plate respectively, and the exhaust holes are formed in the third sealing surface and/or the fourth sealing surface.

In this technical scheme, when the quantity of cylinder is more than or equal to 2, except that set up first bearing and second bearing at axial both ends, the laminating sets up first baffle between two adjacent cylinders, the region that the both sides of first baffle correspond with axial opening respectively forms third sealing surface and fourth sealing surface, through seting up the exhaust hole on third sealing surface and/or fourth sealing surface, realized by the carminative function in compression mechanism middle part.

Wherein, first baffle can include two first sub-baffles and the second sub-baffle that set up along eccentric rotary piston's axial laminating, compression mechanism's spare part is at least including the first bearing that from top to bottom laminates the setting in proper order, the cylinder subassembly, second bearing and first amortization casing, wherein, the cylinder subassembly includes two at least cylinders that set up side by side along the axial, and set up two sub-baffles between two adjacent cylinders, the exhaust hole that switches on with the working chamber of upper portion cylinder can be seted up to first sub-baffle, the exhaust hole that switches on with the working chamber of lower part cylinder can be seted up to the second sub-baffle.

The compression mechanism comprises at least two cylinders, the compression mechanism encloses into at least two working chambers, each working chamber is provided with an exhaust hole, the working chambers are separated by a partition plate, the volumes of the working chambers can be equal or unequal, and the compression mechanism can stably run at a high rotating speed due to good force balance characteristic, so that the application of a double-cylinder or multi-cylinder compression structure in a high-rotating-speed compressor is realized.

In any of the above technical solutions, preferably, the exhaust hole is opened on an inner side wall of the cavity.

In this technical scheme, through offer on the inside wall of cavity with the exhaust hole, compare with the exhaust hole of offering on bearing and baffle that the exhaust hole is axial, when guaranteeing mechanism's intensity, can further increase exhaust area through offering the exhaust hole.

In any of the above technical solutions, preferably, the cylinder assembly further includes: slide assembly, including gleitbretter and elastomer, the gleitbretter sets up in the cavity along the axial, the one end of gleitbretter laminates with eccentric rotary piston's lateral wall, in order to separate the working chamber for first working chamber and second working chamber, the exhaust hole sets up in first working chamber, be provided with the inlet port in the second working chamber, the other end and the one end of elastomer of gleitbretter are connected, the other end of elastomer is fixed in the assigned position, wherein, when eccentric rotary piston rotates, the elastomer passes through elastic deformation and drives gleitbretter reciprocating motion, so that the relative lateral wall of gleitbretter slides, and realize compressing the gas in the first working chamber.

In this technical scheme, install the gleitbretter in the cylinder cavity under the effect of spring force, make its one end always contact the laminating with eccentric piston's lateral wall to can divide into A, B two not communicating cavities of each other with crescent working chamber, wherein, A, B cavity is respectively for breathing in the room and compress the exhaust chamber, the total volume of A, B cavity is the volume of working chamber, seted up into, the gas vent on cylindrical cylinder inside wall.

In any of the above technical solutions, preferably, the method further includes: and the exhaust valve is arranged in the exhaust hole, wherein when the pressure of the gas is higher than the exhaust pressure, the exhaust valve is opened, and the gas is exhausted from the working cavity.

In the technical scheme, by arranging the exhaust valve, when the exhaust pressure is detected to reach the preset pressure threshold, the exhaust valve plate is pushed open, so that the compressed gas is discharged from the working cavity.

In any one of the above technical solutions, preferably, when the exhaust hole is opened on the first closing surface, the compression mechanism further includes: the muffler sets up on the terminal surface that the second bearing was kept away from to first bearing, and the muffler is provided with the amortization chamber, and the amortization chamber can be through exhaust hole and working chamber intercommunication, and wherein, gaseous follow working chamber along exhaust hole row to amortization chamber, discharges after the amortization of amortization chamber.

In this technical scheme, through setting up the muffler, the muffler is provided with the amortization chamber, and gas is discharged to the amortization chamber along the exhaust hole from the working chamber, discharges after amortization through the amortization chamber, has reduced exhaust noise, has promoted compressing mechanism's performance.

Specifically, compression mechanism includes rotating crankshaft, first bearing and the second bearing that supports with rotating crankshaft cooperation, establish the muffler in first bearing top, establish the cylinder between first bearing and second bearing, the eccentric rotary piston of revolution in the cavity of cylinder, with piston complex gleitbretter, act on the spring that makes the gleitbretter paste tight piston on the gleitbretter, the working chamber is enclosed by the cylinder, first bearing, second bearing and piston, the exhaust hole is seted up on first bearing, the high-pressure gas that the compression was accomplished discharges the inner chamber of muffler from the working chamber through the exhaust hole, discharge the inner chamber of casing through the inner chamber of muffler again.

In any of the above technical solutions, preferably, the cylinder assembly further includes: the at least one second partition plate is arranged in the cavity along the axial direction of the eccentric rotary piston, the cavity is divided into at least two sub-inner cavities by the at least one second partition plate, and the eccentric rotary piston is arranged in any one sub-inner cavity to form at least two working cavities.

In the technical scheme, at least one second partition plate is axially arranged in the cavity and divides the cavity into at least two sub-inner cavities, and an eccentric rotary piston is arranged in any one sub-inner cavity, so that the performance of the compression mechanism is further improved.

In any of the above technical solutions, preferably, when the exhaust hole is a variable cross-section hole, the cross-sectional area of the exhaust hole is the area of the smallest cross-section.

In any of the above technical solutions, preferably, when the cavity is a cylindrical cavity, the eccentric rotary piston is a cylindrical piston, and the exhaust hole is a circular hole with a uniform cross section, the diameter of the cylindrical cavity is d₁The diameter of the cylindrical piston being d₂The height of the cylindrical cavity is h, and the aperture of the circular hole with the equal section is d₃And V and S satisfy:

in this solution, the inner diameter of the cylinder is d₁The outer diameter of the piston is d₂The height of the cylinder is h, and the volume of the working cavity is equal to

The diameter of the vent hole is d₃The section area of the exhaust hole is equal to

The determination of the volume and the cross-sectional area of the cavity is realized when the cavity is a cylindrical cavity and the eccentric rotary piston is a cylindrical piston and the exhaust hole is a circular hole with equal cross section.

For example, in the case of a single cylinder compression mechanism, the inner diameter d of the cylinder₁46mm, outside diameter d of the eccentric rotary piston₂38mm, the height h of the cylinder 10 is 20mm, and the volume V of the working cavity of the compressor is 10.555 multiplied by 10³(mm³)。

Calculating the sectional area S of the exhaust hole to be 75.39mm according to that V/S is more than or equal to 60mm and less than or equal to 140mm²≤S≤175.92mm²Diameter d of the vent hole₃ 9.80mm≤d₃Not more than 14.97mm, and the compression mechanism has small exhaust resistance loss and high performance.

In any of the above solutions, preferably, V is 25000mm or more³When, V and S satisfy:

in the technical scheme, the volume of all working cavities is more than or equal to 25000mm³In the process, because the rated rotating speed of the compression mechanism of the rotary compressor is hardly higher than 150rps (because the larger the volume of the working cavity is, the more difficult the reliability under the high rotating speed is to ensure), and the section area of the exhaust hole is large, the exhaust hole is not easy to open, the range of V/S can be reduced to be more than or equal to 80mm and less than or equal to 140 mm.

In any of the above solutions, preferably, V is no more than 15000mm³When, V and S satisfy:

in the technical scheme, the volume of all working cavities is less than or equal to 15000mm³However, since the rated rotation speed of the compression mechanism of the rotary compressor is likely to be higher than 150rps or more (since the smaller the volume of the working chamber, the higher the operational reliability of the compressor at a high rotation speed), the range of V/S can be reduced to 60mm or more and 120mm or less.

In any of the above technical solutions, preferably, when the gas is R410A, the exhaust pressure is 2.542MPa, and the sound velocity of the gas in the exhaust state is 197 m/s; when the gas is R290, the exhaust pressure is 1.445MPa, and the sound velocity of the gas in an exhaust state is 250 m/s; when the gas is R32, the exhaust pressure is 2.620MPa, and the sound velocity of the gas in the exhaust state is 243 m/s.

In the technical scheme, for the compressor, the larger the working volume is, the higher the rotating speed is, the smaller the sound velocity of the gas is, the larger the sectional area of the required exhaust hole is, and the relation between the four is described by introducing a dimensionless parameter, namely an exhaust average mach number M, namely:

wherein V (mm)³) Is the sum of the volumes of all working chambers, S (mm)²) F (rps) is the rated rotating speed of the compressor, C (M/s) is the sound velocity in the exhaust state, and the performance of the compressor is optimal only when the average Mach number M of the exhaust is in a specified range.

An embodiment of a second aspect of the present invention provides a rotary compressor, including: a compressor housing; the crankshaft is arranged in the compressor shell; the driving mechanism is arranged in the compressor shell, the driving assembly comprises a stator and a rotor which are assembled in a matching way, and the rotor is sleeved and connected with one end of the crankshaft; the compression mechanism according to any one of the first aspect of the present invention is disposed in the compressor housing and arranged with the driving mechanism in the axial direction of the crankshaft, and the compression mechanism is connected to the other end of the crankshaft.

In this technical scheme, the rotary compressor can be flexibly set as a swing type rotary compressor or a rolling piston type rotary compressor, and the driving mechanism can be flexibly set as an inner rotor type motor or an outer rotor type motor.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

fig. 1 illustrates a schematic configuration of a rotary compressor according to an embodiment of the present invention;

FIG. 2 is a schematic cross-sectional structural view showing a cross-section of a working chamber of a compression mechanism according to an embodiment of the present invention;

fig. 3 shows a graph of the refrigeration efficiency versus V/S of the compression mechanism according to an embodiment of the present invention.

Wherein, the correspondence between the reference numbers and the component names in fig. 1 and fig. 2 is:

102 cylinders, 104 eccentric rotary pistons, 106 working chambers, 108 exhaust holes, 110 first bearings, 112 second bearings, 114 sliding sheets, 116 elastomers, 118 exhaust valves, 120 silencers, 122 compressor shells, 124 crankshafts, 126 rotors and 128 stators.

Detailed Description

In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.

A compression mechanism according to some embodiments of the present invention is described below with reference to fig. 1 to 3.

As shown in fig. 1 and 2, a compression mechanism according to an embodiment of the present invention includes: the cylinder assembly comprises at least one cylinder 102, and an eccentric rotary piston 104 is correspondingly arranged in a cavity of each cylinder 102; at least one supporting component, with every cylinder 102 subassembly cooperation setting to the closed cavity body, wherein, the inside wall of cavity, the lateral wall of eccentric rotary piston 104 and the closed surface of supporting component enclose and close and form at least one working chamber 106, and at least one exhaust hole 108 has been seted up to every working chamber 106, and the sum V of the volume of all working chambers 106 and the sum S of the cross sectional area of all exhaust holes 108 satisfy:

in this embodiment, by limiting the ratio between the sum of the volumes of all the working chambers 106 and the sum of the cross-sectional areas of all the discharge holes 108 to a specified value range, when the rotation speed of the compression mechanism is at a high rotation speed (greater than or equal to 90rps), on the one hand, the discharge resistance loss of the compression mechanism can be reduced, and on the other hand, the operation efficiency of the compression mechanism can be improved, and the noise generated during the operation of the compression mechanism can be reduced.

The motor of the rotary compressor does not need to convert the rotation of the rotor 126 into the reciprocating motion of the piston, but directly drives the rotary piston to rotate to complete the compression of the refrigerant vapor.

The structure of the rotary compressor is mainly characterized in that refrigerant gas is compressed by the action of an eccentric piston, a rotary crankshaft 124 is coaxial with the axis of a cylinder 102, an eccentric wheel is arranged on the rotary crankshaft 124, a thin-wall elastic sleeve supported by high-quality steel is arranged on the eccentric wheel to form an eccentric rotary piston 104, one side of the eccentric rotary piston 104 is always in close contact with the inner side wall of the cylinder 102, and a crescent-shaped working cavity 106 is formed between the outer surface of the eccentric rotary piston 104 and the inner side wall of the cylinder 102.

Specifically, when the rated rotation speed of the rotary compressor is greater than or equal to 90rps, V/S is greater than or equal to 60mm and less than or equal to 140mm, wherein V is the sum of the volumes of all the working chambers 106, and S is the sum of the cross-sectional areas of all the exhaust holes 108, and on the premise that the structure of the existing working chamber 106 is not changed, the high-speed operation of the compression mechanism is realized by adjusting the value range of the cross-sectional area S of the exhaust hole 108.

As shown in FIG. 3, a graph of the cooling efficiency versus V/S of the compression mechanism according to one embodiment of the present invention is shown, in order to keep the range of the exhaust average Mach number M constant when the rated rotation speed is increased to 90rps, the range of V/S is strained to 120 mm. ltoreq. V/S. ltoreq.200 mm, and considering that the higher the rotation speed is, the greater the adverse effect of the exhaust interruption is on the exhaust, and considering that the rated rotation speed is greater than 90rps, the value of V/S should be further decreased, assuming that the volume of three working chambers 106 (9.8X 10) is (9.8X 10)³mm³，22×10³mm³，48×10³mm³) And then, three-dimensional fluid-solid coupling simulation calculation is carried out at three corresponding rotating speeds (90rps/120rps/150rps), and the result shows that when the V/S range is 60 mm-140 mm, the COP (refrigeration efficiency) is the highest, namely the performance of the rotary compressor is higher.

The cross-sectional shape of the vent hole 108 may be circular, oblong, polygonal, etc.

the first embodiment is as follows:

as shown in fig. 1, in the above embodiment, preferably, the support assembly includes: the first bearing 110 and the second bearing 112 are respectively attached to two outer end faces of the cylinder 102 assembly, the outer end faces have axial openings of the working chamber 106, a first closed face is formed in a region of the first bearing 110 corresponding to the axial openings, a second closed face is formed in a region of the second bearing 112 corresponding to the axial openings, and the exhaust hole 108 is formed in the first closed face and/or the second closed face.

In this embodiment, the support assembly is configured to include the first bearing 110 and the second bearing 112, that is, when the support assembly is configured as the single cylinder 102, the first bearing 110 and the second bearing 112 are respectively disposed at two ends of the single cylinder 102, a region of the first bearing 110 corresponding to the axial opening forms a first closed surface, a region of the second bearing 112 corresponding to the axial opening forms a second closed surface, and the exhaust hole 108 is opened on the first closed surface and/or the second closed surface, so that the compressed gas of the single cylinder 102 compressor is exhausted.

The first bearing 110 is a main bearing, the second bearing 112 is an auxiliary bearing, only one exhaust hole 108 is arranged on the main bearing, or a plurality of exhaust holes 108 are arranged on the first bearing 110 and the second bearing 112 respectively, and the compression mechanism is accelerated by increasing the area of the exhaust hole 108 on the premise that the V/S is more than or equal to 60mm and less than or equal to 140 mm.

Specifically, considering the eccentricity of the eccentric rotary piston 104 and the utilization rate of the exhaust area, the sectional area of a single exhaust hole 108 cannot be designed to be too large, and often two or more exhaust holes 108 are formed in one working chamber 106, and the sectional areas of the exhaust holes 108 may be equal or unequal.

For example, in the single cylinder 102 compression mechanism, two exhaust holes 108 having the same diameter are opened in the working chamber 106, and when the exhaust holes 108 are circular holes, the volume V of the working chamber 106 of the compressor is 10.555 × 10³(mm³) When the diameter of the vent hole 108 is larger than or equal to 4.90 multiplied by 10^-3m, and less than or equal to 7.48X 10^-3m。

Example two:

in any of the above embodiments, preferably, when the number of the cylinders 102 is greater than or equal to 2, and the plurality of cylinders 102 are arranged side by side in the axial direction, the support assembly further includes: the first partition plate is attached to and arranged between any two adjacent cylinders 102, an axial opening is formed in the attaching surface of any two adjacent cylinders 102 and the first partition plate, a third sealing surface and a fourth sealing surface are formed in the regions, corresponding to the axial opening, of the two sides of the first partition plate respectively, and the exhaust holes 108 are formed in the third sealing surface and/or the fourth sealing surface.

In this embodiment, when the number of the cylinders 102 is greater than or equal to 2, in addition to providing the first bearing 110 and the second bearing 112 at both ends in the axial direction, a first partition plate is disposed between two adjacent cylinders 102 in a fitting manner, regions of both sides of the first partition plate corresponding to the axial openings respectively form a third closed surface and a fourth closed surface, and the exhaust hole 108 is formed in the third closed surface and/or the fourth closed surface, so that the function of exhausting air from the middle of the compression mechanism is achieved.

Wherein, the first baffle can include two first sub-baffles and the second sub-baffles that set up along the axial laminating of eccentric rotary piston 104, the spare part of compressing mechanism is including laminating the first bearing 110 that sets up from top to bottom in proper order at least, cylinder 102 subassembly, second bearing 112 and first amortization casing, wherein, cylinder 102 subassembly includes two at least cylinders 102 that set up side by side along the axial, and set up two sub-baffles between two adjacent cylinders 102, the exhaust hole 108 that switches on with the working chamber 106 of upper portion cylinder 102 can be seted up to first sub-baffle, the exhaust hole 108 that switches on with the working chamber 106 of lower part cylinder 102 can be seted up to the second sub-baffle.

The compression mechanism comprises at least two cylinders 102, the compression mechanism encloses at least two working chambers 106, each working chamber 106 is provided with an exhaust hole 108, the working chambers 106 are separated by partition plates, the volumes of the working chambers 106 can be equal or unequal, and the compression mechanism can stably run at a high rotating speed due to good force balance characteristic, so that the application of a double-cylinder or multi-cylinder compression structure in a high-rotating-speed compressor is realized.

Example three:

in any of the above embodiments, preferably, the vent hole 108 opens on the inner side wall of the cavity.

In this embodiment, by forming the exhaust hole 108 on the inner side wall of the cavity, compared with the exhaust hole 108 formed on the bearing and the partition plate, which are both axial, the exhaust area can be further increased by forming the exhaust hole 108 while ensuring the strength of the mechanism.

As shown in fig. 1 and 2, in any of the above embodiments, preferably, the cylinder 102 assembly further includes: slide assembly, including gleitbretter 114 and elastomer 116, gleitbretter 114 sets up in the cavity along the axial, the one end of gleitbretter 114 and the lateral wall laminating of eccentric rotary piston 104, in order to separate working chamber 106 for first working chamber 106 and second working chamber 106, exhaust hole 108 sets up in first working chamber 106, be provided with the inlet port in the second working chamber 106, the other end and the one end of elastomer 116 of gleitbretter 114 are connected, the other end of elastomer 116 is fixed in the assigned position, wherein, when eccentric rotary piston 104 rotated, elastomer 116 drove gleitbretter 114 reciprocating motion through elastic deformation, so that the relative lateral wall of gleitbretter 114 slides, and realize compressing the gas in the first working chamber 106.

In this embodiment, the sliding piece 114 installed in the cavity of the cylinder 102 has one end always contacting and fitting with the outer sidewall of the eccentric piston under the action of the spring force, so as to divide the crescent-shaped working cavity 106 into A, B two chambers which are not communicated with each other, wherein, A, B chambers are respectively a suction chamber and a compression exhaust chamber, A, B chambers have a total volume equal to the volume of the working cavity 106, and an air inlet and an air outlet are opened on the inner sidewall of the cylindrical cylinder 102.

As shown in fig. 1, in any of the above embodiments, preferably, the method further includes: and an exhaust valve 118 disposed in the exhaust port 108, wherein when the pressure of the gas is greater than the exhaust pressure, the exhaust valve 118 opens and the gas is exhausted from the working chamber 106.

In this embodiment, by providing the exhaust valve 118, the discharge of compressed gas from the working chamber 106 is achieved by urging the exhaust valve 118 open when it is detected that the exhaust pressure has reached a predetermined pressure threshold.

In any of the above embodiments, as shown in fig. 1, preferably, when the gas discharge hole 108 is opened on the first closing surface, the compression mechanism further includes: muffler 120, set up on the terminal surface that first bearing 110 kept away from second bearing 112, muffler 120 is provided with the amortization chamber, and the amortization chamber can be through exhaust hole 108 and working chamber 106 intercommunication, and wherein, gaseous follow working chamber 106 is arranged to the amortization chamber along exhaust hole 108, discharges after the amortization through the amortization chamber.

In this embodiment, by providing the muffler 120, the muffler 120 is provided with a silencing chamber, and the gas is exhausted from the working chamber 106 to the silencing chamber along the exhaust hole 108, and is exhausted after being silenced by the silencing chamber, so that the exhaust noise is reduced, and the performance of the compression mechanism is improved.

Specifically, the compression mechanism includes a rotating crankshaft 124, a first bearing 110 and a second bearing 112 cooperatively supported with the rotating crankshaft 124, a muffler 120 disposed above the first bearing 110, a cylinder 102 disposed between the first bearing 110 and the second bearing 112, an eccentric rotary piston 104 revolving in a cavity of the cylinder 102, a sliding vane 114 cooperating with the piston, and a spring acting on the sliding vane 114 to make the sliding vane 114 closely contact with the piston, a working chamber 106 is defined by the cylinder 102, the first bearing 110, the second bearing 112, and the piston, an exhaust hole 108 is disposed on the first bearing 110, and compressed high-pressure gas is exhausted from the working chamber 106 to an inner chamber of the muffler 120 through the exhaust hole 108 and then exhausted to an inner chamber of the housing through an inner chamber of the muffler 120.

Example four:

in any of the above embodiments, preferably, the cylinder 102 assembly further comprises: at least one second partition board is arranged in the cavity along the axial direction of the eccentric rotary piston 104, the cavity is divided into at least two sub-inner cavities by the at least one second partition board, and the eccentric rotary piston 104 is arranged in any one sub-inner cavity to form at least two working cavities 106.

In this embodiment, the performance of the compression mechanism is further enhanced by providing at least one second partition axially disposed within the chamber, the at least one second partition dividing the chamber into at least two sub-chambers, and an eccentric rotary piston 104 disposed within any one of the sub-chambers.

In any of the above embodiments, preferably, when the exhaust hole 108 is a variable cross-section hole, the cross-sectional area of the exhaust hole 108 is the area of the smallest cross-section.

In any of the above embodiments, as shown in fig. 2, preferably, when the cavity is a cylindrical cavity, the eccentric rotary piston 104 is a cylindrical piston, and the exhaust hole 108 is a circular hole with a constant cross section, the diameter of the cylindrical cavity is d₁The diameter of the cylindrical piston being d₂The height of the cylindrical cavity is h, and the aperture of the circular hole with the equal section is d₃And V and S satisfy:

in this embodiment, the cylinder 102 has an inner diameter d₁The outer diameter of the piston is d₂The height of the cylinder 102 is h, and the volume of the working chamber 106 is equal to

The diameter of the vent hole 108 is d₃The cross-sectional area of the exhaust hole 108 is equal to

The determination of the volume and the cross-sectional area of the cavity is realized when the cavity is a cylindrical cavity and the eccentric rotary piston 104 is a cylindrical piston and the exhaust hole 108 is a circular hole with the same cross section.

For example, taking the single cylinder 102 compression mechanism as an example, the cylinderInner diameter d of 102₁46mm, outside diameter d of eccentric rotary piston 104₂38mm, height h of the cylinder 10210 is 20mm, and the volume V of the working chamber 106 of the compressor is 10.555 × 10³(mm³)。

According to the V/S of more than or equal to 60mm and less than or equal to 140mm, the cross-sectional area S of the exhaust hole 108 is calculated to be 75.39mm²≤S≤175.92mm²Diameter d of the vent hole 108₃ 9.80mm≤d₃Not more than 14.97mm, and the compression mechanism has small exhaust resistance loss and high performance.

Example five:

in any of the above embodiments, preferably, at V ≧ 25000mm³When, V and S satisfy:

in this embodiment, the volume of all the working chambers 106 is 25000mm or more³In the case that the rated rotation speed of the compression mechanism of the rotary compressor is hardly higher than 150rps (since the larger the volume of the working chamber 106 is, the more difficult the reliability at high rotation speed is to be secured), and the sectional area of the exhaust hole 108 is large and the exhaust hole 108 is not easily opened, the V/S range can be reduced to 80mm or more and 140mm or less.

Example six:

in any of the above embodiments, preferably, V ≦ 15000mm³When, V and S satisfy:

in this embodiment, the volume of all the working chambers 106 is less than or equal to 15000mm³However, since the rated rotation speed of the compression mechanism of the rotary compressor is likely to be higher than 150rps (since the smaller the volume of the working chamber 106, the higher the reliability of the operation of the compressor at high rotation speed), the V/S range can be reduced to 60mm or more and 120mm or less.

In any of the above embodiments, preferably, when the gas is R410A, the exhaust pressure is 2.542MPa, and the sound velocity of the gas in the exhaust state is 197 m/s; when the gas is R290, the exhaust pressure is 1.445MPa, and the sound velocity of the gas in an exhaust state is 250 m/s; when the gas is R32, the exhaust pressure is 2.620MPa, and the sound velocity of the gas in the exhaust state is 243 m/s.

In this embodiment, for the compressor, the larger the displacement volume, the higher the rotational speed, the smaller the sound velocity of the gas, and the larger the cross-sectional area of the required exhaust port 108, the relationship between which is described by introducing a dimensionless parameter, the average mach number M of the exhaust, namely:

wherein V (mm)³) Is the sum of the volumes of all working chambers 106, S (mm)²) The sum of the cross-sectional areas of all the discharge ports 108, f (rps) is the rated speed of the compressor, and C (M/s) is the sound velocity in the discharge state, and the performance of the compressor is optimized only when the discharge average mach number M is within a specified range.

As shown in fig. 1, a rotary compressor according to an embodiment of the present invention includes: a compressor housing 122; a crankshaft 124 disposed within the compressor housing 122; the driving mechanism is arranged in the compressor shell 122, the driving component comprises a stator 128 and a rotor 126 which are assembled in a matching way, and the rotor 126 is sleeved and connected with one end of the crankshaft 124; the compression mechanism according to any one of the first aspect of the present invention is disposed in the compressor housing 122 and arranged with the driving mechanism along the axial direction of the crankshaft 124, and the compression mechanism is connected to the other end of the crankshaft 124.

In this embodiment, the rotary compressor may be flexibly configured as a swing type rotary compressor or a rolling piston type rotary compressor, and the driving mechanism may be flexibly configured as an inner rotor type motor or an outer rotor type motor.

In the present invention, the terms "first", "second", and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the term "plurality" means two or more unless expressly limited otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the description of the present invention, it is to be understood that the terms "upper", "lower", "left", "right", "front", "rear", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the referred device or unit must have a specific direction, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention.

In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes will occur to those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A compression mechanism, comprising:

the cylinder assembly comprises at least one cylinder, and an eccentric rotary piston is correspondingly arranged in a cavity of each cylinder;

at least one supporting component which is matched with each cylinder component and seals the cavity,

wherein, the inside wall of cavity, the lateral wall of eccentric rotary piston and the seal surface of supporting component enclose to close and form at least one working chamber, every at least one exhaust hole has been seted up to the working chamber, all the volume sum V of working chamber, and all the cross sectional area sum S in exhaust hole satisfies:

；

v is more than or equal to 25000mm³When, V and S satisfy:

；

v is less than or equal to 15000mm³When, V and S satisfy:

；

the support assembly includes:

the first bearing and the second bearing are respectively attached to two outer side end faces of the air cylinder assembly, the outer side end faces are provided with axial openings of the working cavity, a first closed face is formed in the area of the first bearing corresponding to the axial openings, a second closed face is formed in the area of the second bearing corresponding to the axial openings,

the exhaust hole is formed in the first sealing surface and/or the second sealing surface;

the exhaust hole is formed in the inner side wall of the cavity;

when the exhaust hole is opened on the first closed surface, the compression mechanism further includes: the silencer is arranged on the end surface of the first bearing far away from the second bearing and is provided with a silencing cavity which can be communicated with the working cavity through the exhaust hole,

and the gas is exhausted from the working cavity to the silencing cavity along the exhaust hole, and is exhausted after being silenced by the silencing cavity.

2. The compression mechanism as claimed in claim 1, wherein the number of the cylinders is greater than or equal to 2, and the cylinders are arranged side by side in the axial direction, and the support assembly further comprises:

the first partition board is attached and arranged between any two adjacent cylinders, the attachment surface of any two adjacent cylinders and the first partition board is provided with the axial opening, and the areas of the two sides of the first partition board, which correspond to the axial opening respectively, form a third closed surface and a fourth closed surface,

wherein the exhaust hole is formed on the third closing surface and/or the fourth closing surface.

3. The compression mechanism of claim 1, wherein the cylinder assembly further comprises:

the sliding sheet assembly comprises a sliding sheet and an elastic body, the sliding sheet is arranged in the cavity along the axial direction, one end of the sliding sheet is attached to the outer side wall of the eccentric rotary piston so as to divide the working cavity into a first working cavity and a second working cavity, the exhaust hole is arranged in the first working cavity, an air inlet hole is arranged in the second working cavity, the other end of the sliding sheet is connected with one end of the elastic body, and the other end of the elastic body is fixed at a designated position,

when the eccentric rotary piston rotates, the elastic body drives the sliding sheet to reciprocate through elastic deformation, so that the sliding sheet slides relative to the outer side wall, and gas in the first working cavity is compressed.

4. The compression mechanism as set forth in claim 3, further comprising:

an exhaust valve arranged in the exhaust hole,

when the pressure of the gas is higher than the exhaust pressure, the exhaust valve is opened, and the gas is exhausted from the working cavity.

5. The compression mechanism of claim 1, wherein the cylinder assembly further comprises:

at least one second partition board is arranged in the cavity along the axial direction of the eccentric rotary piston, the cavity is divided into at least two sub-inner cavities by the at least one second partition board, and the eccentric rotary piston is arranged in any one of the sub-inner cavities to form at least two working cavities.

6. The compression mechanism of claim 1,

when the vent hole is a variable cross-section hole, the cross-sectional area of the vent hole is the area of the smallest cross-section.

7. A compression mechanism as claimed in any one of claims 1 to 5, wherein when the chamber is a cylindrical chamber and the eccentric rotary piston is a cylindrical piston, and the discharge orifice is a circular orifice of constant cross-section, the diameter of the cylindrical chamber is d₁The diameter of the cylindrical piston is d₂The height of the cylindrical cavity is h, and the aperture of the circular hole with the uniform section is d₃And V and S satisfy:

。

8. the compression mechanism of claim 4,

when the gas is R410A, the exhaust pressure is 2.542MPa, and the sound velocity of the gas in an exhaust state is 197 m/s;

when the gas is R290, the exhaust pressure is 1.445MPa, and the sound velocity of the gas in the exhaust state is 250 m/s;

when the gas is R32, the exhaust pressure is 2.620MPa, and the sound velocity of the gas in the exhaust state is 243 m/s.

9. A rotary compressor, comprising:

a compressor housing;

a crankshaft disposed within the compressor housing;

the driving mechanism is arranged in the compressor shell and comprises a stator and a rotor which are assembled in a matching way, and the rotor is sleeved and connected with one end of the crankshaft;

the compression mechanism according to any one of claims 1 to 8, disposed in the compressor housing and arranged with the drive mechanism in an axial direction of the crankshaft, the compression mechanism being connected to the other end of the crankshaft.