CN111720319B

CN111720319B - Compression mechanism of rotary compressor

Info

Publication number: CN111720319B
Application number: CN202010605974.8A
Authority: CN
Inventors: 罗承卓; 谭琴
Original assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Current assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Priority date: 2020-06-29
Filing date: 2020-06-29
Publication date: 2021-11-23
Anticipated expiration: 2040-06-29
Also published as: CN111720319A

Abstract

The invention discloses a compression mechanism of a rotary compressor. The compression mechanism includes: each cylinder is internally provided with a cylinder chamber and a slide sheet groove, a piston is arranged in each cylinder chamber, a slide sheet is arranged in each slide sheet groove, the slide sheet can move in a reciprocating mode between an inner limit position and an outer limit position, each cylinder chamber is provided with an exhaust hole communicated with the cylinder chamber, and each exhaust hole is provided with an exhaust valve sheet; the transmission part drives the exhaust valve plates to close the exhaust holes when the sliding sheet moves outwards, wherein the rigidity of each exhaust valve plate is K, the unit is N/mm, and the sum of the volumes of the cylinder chambers is V_sumMillimeter³Sum of stiffness K of the exhaust flap_sum(ii) a When the refrigerant is R134a or R290, 80000 mm⁴V is less than or equal to ox_sum/K_sumLess than or equal to 350000 mm⁴A/cow; when the refrigerant is other than R134a or R290, 50000mm⁴V is less than or equal to ox_sum/K_sumLess than or equal to 200000 mm⁴A/cattle. According to the compression mechanism provided by the invention, the exhaust valve plate is closed in time, and the compression mechanism has the advantages of good applicability and reliability, low noise and high energy efficiency.

Description

Compression mechanism of rotary compressor

Technical Field

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

Background

The exhaust valve plate is an important part of the rotary compressor, and influences the energy efficiency, power consumption, noise and the like of the compressor. Various improvements to the structure and material of the exhaust valve sheet itself have been proposed in the related art, but these improvements have respective problems, and thus there is a need for improvement.

Disclosure of Invention

The present invention is based on the discovery and recognition by the inventors of the following facts and problems:

in the related art, the discharge valve plate of the rotary compressor is generally a reed valve plate having a certain elasticity, i.e., a certain rigidity, and one end of the discharge valve plate is fixed and the other end is free to open and close the discharge hole.

The inventor finds and realizes through research that the greater the rigidity of the exhaust valve plate, the better the closure timeliness of the exhaust valve, and the higher the reliability, the lower the noise impacting the valve seat. However, the larger the rigidity of the exhaust valve plate is, the slower the opening is, the smaller the opening amplitude is, the smaller the exhaust flow area is, the larger the exhaust resistance loss is, the larger the power consumption of the compressor is, and thus the rigidity design of the exhaust valve plate is difficult, the design flexibility is limited, and the applicability and reliability of the exhaust valve plate are poor.

In the related art, the rigidity of the exhaust valve plate is usually designed according to the gas thrust force applied to the exhaust valve plate, but the exhaust valve plate designed in the way cannot adapt to different compressors and different working conditions of the compressors. For example, for a variable frequency compressor, the rotating speed of the variable frequency compressor is variable, when the compressor runs at a high speed, more gas is discharged in unit time, the acting force of the gas on the exhaust valve plate is larger, and in order to ensure that the exhaust valve plate is closed in time, avoid backflow to influence energy efficiency and reduce noise, the exhaust valve plate needs to be designed to have larger rigidity; when the compressor runs at a low speed, the gas acting force on the exhaust valve plate is small, the exhaust valve plate with high rigidity cannot ensure the full opening of the exhaust valve plate, so that the flutter is easy to occur, the exhaust resistance loss is large, and the noise problem caused by the airflow pulsation is easy to cause. Therefore, when the compressor is operated at a variable speed, the discharge valve sheet is generally designed to have a large rigidity in order to ensure reliability of the discharge valve sheet, but this inevitably results in an influence on the energy efficiency of the compressor at a low speed. In order to improve the energy efficiency of the compressor, if the discharge valve plate is designed to have a low rigidity, the problems of reduced closing timeliness and reliability of the compressor at high rotation speed and high noise are caused.

Therefore, the inventor has realized that the difficulty in designing the rigidity of the exhaust valve sheet cannot be solved only by improving the structure and material of the exhaust valve sheet itself, resulting in the problem of poor design flexibility, applicability, and reliability of the exhaust valve sheet.

The present invention is directed to solving, at least to some extent, one of the technical problems in the related art.

Therefore, the embodiment of the invention provides a compression mechanism, and the exhaust valve plate of the compression mechanism is good in closing timeliness, applicability and reliability, low in noise and high in energy efficiency.

The embodiment of the invention also provides a rotary compressor comprising the compression mechanism.

The embodiment of the invention also provides a refrigerating device comprising the compressor.

The compression mechanism comprises at least one cylinder, wherein each cylinder is internally provided with a cylinder chamber and a slide sheet groove, a piston is arranged in the cylinder chamber, a slide sheet is arranged in the slide sheet groove, the inner end of the slide sheet is abutted against the piston, the slide sheet can reciprocate between an inner limit position and an outer limit position, the cylinder chamber is provided with an exhaust hole communicated with the cylinder chamber, and an exhaust valve plate is configured on the exhaust hole and used for opening and closing the exhaust hole; a crankshaft for driving the piston to eccentrically rotate within the cylinder chamber to compress refrigerant; an upper bearing and a lower bearing rotatably supporting the crankshaft, the upper bearing closing an upper end of the cylinder chamber, the lower bearing closing a lower end of the cylinder chamber; the transmission component drives the exhaust valve plates to close the exhaust holes when the slide sheet moves outwards, the rigidity of each exhaust valve plate is K, the unit is N/mm, when K is equal to the projection point of the central axis of each exhaust hole on the exhaust valve plates and rises by 1 mm in value, force needs to be applied to the projection point along the central axis of each exhaust hole, and the sum of the volumes of the cylinder chambers is V_sumMillimeter³Sum of stiffness K of the exhaust valve sheet_sumWherein the following relationship is satisfied: when the refrigerant is R134a or R290, 80000 mm⁴V is less than or equal to ox_sum/K_sumLess than or equal to 350000 mm⁴A/cow; when the refrigerant is other than R134a or R290, 50000mm⁴V is less than or equal to ox_sum/K_sumLess than or equal to 200000 mm⁴A/cattle.

According to the compression mechanism provided by the embodiment of the invention, when the slide sheet moves from the inner limit position to the outer limit position, namely the slide sheet moves along the center far away from the cylinder chamber, the transmission part applies closing force for closing the exhaust hole to the exhaust valve sheet, namely the exhaust valve sheet is pushed to close the exhaust hole, and the exhaust valve sheet closes the exhaust hole by virtue of the thrust of the transmission part, so that the closing timeliness and reliability of the exhaust valve sheet can be improved, the rigidity of the exhaust valve sheet can be designed to be smaller, the opening is easy, the exhaust resistance loss is reduced, the design flexibility and applicability of the exhaust valve sheet are improved, and the exhaust noise is reduced.

In some embodiments, 5000 mm thereof³≤V_sumLess than or equal to 16000 mm³。

In some embodiments, the compression mechanism of claim 1, further comprising a lift stopper configured to limit a lift of the exhaust valve plate, the exhaust valve plate includes a fixed end, a free end, and a waist portion located between the fixed end and the free end, the fixed end of the exhaust valve plate is provided with a first mounting hole, the lift stopper is disposed on the exhaust valve plate and includes a horizontal section and a curved section, the horizontal section is provided with a second mounting hole, the exhaust valve plate and the lift stopper are mounted together by a fastener passing through the first mounting hole and the second mounting hole, a distance from a center of the exhaust hole to a center of the first mounting hole is L mm, a distance from a center of the second mounting hole to a junction of the curved section and the horizontal section is L1 mm, a width of the waist portion is B mm, and a thickness of the exhaust valve plate is T mm, the elastic modulus of the exhaust valve plate is E N/mm²The rigidity of the exhaust valve plate is K newtons per millimeter, wherein:

in some embodiments, where 120 ≦ L/T ≦ 200.

In some embodiments, 0.3 mm²T multiplied by B is less than or equal to 0.8 mm²。

In some embodiments, the cylinder chamber is a cylindrical cavity with a diameter d1, the piston is a cylindrical cavity with a diameter d2, the height of the cylinder chamber is h, and the working chamber volume is V, wherein

In some embodiments, the transmission member contacts the vent valve plate when the slide is at the inner limit position or contacts the vent valve plate after the slide moves outward from the inner limit position by a predetermined distance to drive the vent valve plate to close the vent hole.

In some embodiments, the transmission component is a swing rod, and the swing rod is driven to swing around a pivot when the slide sheet moves outwards, so that the swing rod drives the exhaust valve sheet to close the exhaust hole.

In some embodiments, the swing rod includes a rod body, a sliding piece contact portion, and a valve plate contact portion, and when the sliding piece moves outward, the rod body is driven to swing by pushing the sliding piece contact portion, so that the valve plate contact portion drives the exhaust valve plate to close the exhaust hole.

In some embodiments, the transmission component includes a main translational part and an auxiliary translational part, the slide plate drives the main translational part to translate when moving outwards, and the main translational part drives the auxiliary translational part to translate so that the auxiliary translational part drives the exhaust valve plate to close the exhaust hole.

In some embodiments, the primary translational member is provided with a guide surface for driving the secondary translational member, and the guide surface is a slope or an arc surface.

In some embodiments, the secondary translational member contacts the guide surface when the slide is in the inner limit position or after moving outwardly from the inner limit position by a predetermined distance.

The rotary compressor according to the embodiment of the present invention includes the compression mechanism of the above-described embodiment.

The refrigeration device according to the embodiment of the invention comprises the rotary compressor of the above embodiment.

Drawings

Fig. 1 is a sectional view of a compressor according to an embodiment of the present invention.

Fig. 2 is an exploded view of a compression mechanism according to an embodiment of the present invention.

Fig. 3 is a plan view of a compression mechanism according to an embodiment of the present invention.

Fig. 4 is a sectional view taken along B-B in fig. 3.

Fig. 5 is a sectional view taken along C-C in fig. 3.

Fig. 6 is a schematic structural view of a transmission member according to an embodiment of the present invention.

FIG. 7A is a schematic view illustrating the installation of a lift limiter and an exhaust valve plate of a compression mechanism according to an embodiment of the present invention.

FIG. 7B is a schematic diagram of another state of a lift stop and an exhaust valve plate of a compression mechanism according to an embodiment of the present invention.

Fig. 8A is a sectional view of a discharge valve sheet of a compression mechanism according to an embodiment of the present invention.

FIG. 8B is a top view of a discharge plate of a compression mechanism according to an embodiment of the present invention.

Fig. 9 is a state diagram in which the transmission member of the compression mechanism does not contact the discharge valve sheet according to the embodiment of the present invention.

Fig. 10 is a view showing a state where a transmission member of the compression mechanism contacts the discharge valve sheet according to the embodiment of the present invention.

Fig. 11 is a schematic diagram of the compression mechanism according to the embodiment of the present invention, in which the crank angle is 0 ° or 360 °.

Fig. 12 is a schematic view of a compression mechanism according to an embodiment of the present invention having a crank angle of 180 °.

Fig. 13 is an exploded view of a compression mechanism according to another embodiment of the present invention.

Fig. 14 is a schematic top view of a compression mechanism according to another embodiment of the invention.

Fig. 15 is a sectional view taken along D-D in fig. 14.

Fig. 16 is a view showing a state in which a discharge valve sheet is not driven to close a discharge hole by a transmission member of a compression mechanism according to another embodiment of the present invention.

Fig. 17 is a view showing a state in which a discharge valve sheet is driven to close a discharge hole by a driving part of a compression mechanism according to another embodiment of the present invention.

Fig. 18 is a schematic cross-sectional view of the primary translation of the transmission component of the compression mechanism according to another embodiment of the present invention.

Reference numerals:

100. a housing;

200. a motor;

300. a compression mechanism;

1. a cylinder; 101. a cylinder chamber; 102. a slide groove;

2. an exhaust hole;

3. a piston;

4. a crankshaft; 401. an eccentric portion;

5. an upper bearing; 501. accommodating grooves; 5011. a fastener;

6. a lower bearing;

7. sliding blades;

8. an exhaust valve plate; 801. a fixed end; 8011. a first mounting hole; 802. a free end; 803. a waist part; 804. a windward region;

9. a lift limiter; 901. a horizontal segment; 9011. a second mounting hole; 902. a curved section; 9021. avoiding holes; 903. a limiting surface;

10. a swing rod; 1001. a rod body; 1002. a slider contact portion; 1003. a valve sheet contact portion; 1004. a pivot hole;

11. a pivot;

12. a translation component; 1201. a primary translational member; 12011. a first vertical section; 12012. a first horizontal segment 12013, a second vertical segment; 12014. a second horizontal segment; 12015. an inclined section; 12016. a guide surface; 1202. and an auxiliary translation member.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

A compression mechanism 300 and a rotary compressor according to an embodiment of the present invention will be described with reference to fig. 1 to 18.

As shown in fig. 1, the rotary compressor according to the embodiment of the present invention includes a casing 100, a motor 200 and a compression mechanism 300, the motor 200 and the compression mechanism 300 being installed in the casing 100, the motor 200 being used to drive the compression mechanism 300.

A compression mechanism 300 of a rotary compressor according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

As shown in fig. 1 to 18, a compression mechanism 300 according to an embodiment of the present invention includes a cylinder 1, an exhaust hole 2, a piston 3, a crankshaft 4, an upper bearing 5, a lower bearing 6, a vane 7, an exhaust valve plate 8, and a transmission member.

The cylinder 1 has one or more cylinders and has a cylinder chamber 101 and a vane groove 102 inside. The exhaust hole 2 communicates with the cylinder chamber 101, an eccentric portion 401 is provided at one end of the crankshaft 4, and the piston 3 is attached to the eccentric portion 401. The crankshaft 4 is rotatably supported by an upper bearing 5 and a lower bearing 6, and the crankshaft 4 drives the piston 3 to eccentrically rotate in the cylinder chamber 101 to compress the refrigerant, thereby performing compression. The slide plate 7 is movable in a reciprocating manner in the slide plate groove 102, the inner end of the slide plate 7 abuts against the piston 3, the slide plate 7 partitions the cylinder chamber 101 into an intake chamber and an exhaust chamber as the piston 3 eccentrically rotates in the cylinder chamber 101, and the exhaust hole 2 communicates with the exhaust chamber. The vane 7 has an inner limit position and an outer limit position in the vane groove 102, and the vane 7 reciprocates between the inner limit position and the outer limit position in the vane groove 102 as the piston 3 eccentrically rotates in the cylinder chamber 101.

In the embodiment of the present invention, for convenience of description, the term "inner" refers to a direction toward the center of the cylinder chamber 101 in the radial direction of the cylinder chamber 101, and "outer" refers to a direction away from the center of the cylinder chamber 101 in the radial direction of the cylinder chamber 101.

Correspondingly, the end of the sliding sheet 7 close to the piston 3 is the inner end of the sliding sheet 7, the end of the sliding sheet 7 far away from the piston 3 is the outer end of the sliding sheet 7, and the sliding sheet 7 moves outwards, namely the sliding sheet 7 moves from the inner limit position to the outer limit position. For example, in fig. 4, the inward movement of the slider 7 is the leftward movement of the slider 7, and the outward movement of the slider 7 is the rightward movement of the slider 7.

The inner limit position is a position of the vane 7 when the inner end of the vane 7 is closest to the center of the cylinder chamber 101, that is, a position of the vane 7 when the crank angle is 180 degrees, as shown in fig. 12. The outer limit position is a position of the vane 7 when the inner end of the vane 7 is farthest from the center of the cylinder chamber 101, that is, a position of the vane 7 when the crank angle is 0 or 360 degrees, which is a rotation angle of the compressor, as shown in fig. 11.

The discharge valve sheet 8 is used to open and close the discharge hole 2. The transmission component is used for driving the exhaust valve plate 8 to close the exhaust hole 2 when the sliding sheet 7 moves outwards. In other words, the transmission member is linked with the sliding piece 7, and when the sliding piece 7 moves from the inner limit position to the outer limit position, the transmission member drives the exhaust valve piece 8 to close the exhaust hole 2.

The rigidity of each exhaust valve plate 8 is K, and the unit is n/mm, and when K is numerically equal to 1 mm higher than the projection point of the central axis of the exhaust hole 2 on the exhaust valve plate 8, the force needs to be applied to the projection point along the central axis of the exhaust hole 2, as shown in fig. 7B. When there are a plurality of cylinders 1, the sum of the volumes of the cylinder chambers 101 in the plurality of cylinders 1 is V_sumMm 3, sum of rigidity K of plural exhaust valve sheets 8_sumWherein the following relationship is satisfied: when the refrigerant is R134a or R290, then 80000 mm4/N ≤ V_sum/K_sumLess than or equal to 350000 mm 4/cow; when the refrigerant is other than R134a or R290, then 50000mm4/N ≤ V_sum/K_sumLess than or equal to 200000 mm 4/cow.

As shown in fig. 1 to 5, when the compression mechanism 300 operates, the piston 3 eccentrically rotates in the cylinder chamber 101 to compress the refrigerant, the low-temperature and low-pressure gas refrigerant in the cylinder chamber 101 is compressed into a high-temperature and high-pressure gas refrigerant, when the pressure reaches a certain value, the refrigerant pushes the discharge valve plate 8 open and is discharged from the discharge hole 2, the piston 3 pushes the slide plate 7 to move from the inner limit position to the outer limit position, and the transmission member applies a closing force to the discharge valve plate 8 to close the discharge hole 2, so as to drive the discharge valve plate 8 to close the discharge hole 2. Because the exhaust valve plate 8 is pushed by the transmission part to close the exhaust hole 2, the timeliness and the reliability are improved when the exhaust valve plate 8 is closed. Moreover, due to the assistance of the transmission part, the rigidity design of the exhaust valve plate 8 is flexible, and the exhaust valve plate 8 can be designed to be non-rigid (namely the exhaust valve plate 8 is not fixed), so that the exhaust valve plate 8 is easy to open, the opening degree is large, the exhaust resistance is reduced, the exhaust noise is reduced, and high energy efficiency can be ensured at both high speed and low speed.

In addition, the sum V of the volumes of all the cylinder chambers 101_sumAnd the sum K of the rigidity of all the exhaust valve plates 8_sumRatio of (A to (B)The value is limited within the numerical range, and the exhaust resistance loss of the compression mechanism 300 can be reduced and the energy efficiency of the compression mechanism 300 can be improved when the rotation speed of the compression mechanism 300 is at a low speed. Further, V_sum/K_sumIn relation to the force of the refrigerant acting on the discharge valve plate 8. The greater the density of the refrigerant when it is discharged, the greater the force applied to the discharge valve sheet 8, and the greater the rigidity of the discharge valve sheet 8.

The inventors have found through studies that when a refrigerant such as R134a or R290 having a low discharge density is used, V is adjusted to be lower_sum/K_sumV is less than or equal to V at 80000 mm4/N_sum/K_sumAt 350000 mm4/N or less, the compression mechanism 300 is energy efficient. When other refrigerants are used, such as R32 refrigerant, V will be_sum/K_sumV is less than or equal to V at 50000mm 4/cattle_sum/K_sumWhen the compression mechanism 300 is less than or equal to 200000 mm 4/cow, the energy efficiency is high.

Specifically, the inventors conducted comparative experiments on the energy efficiency, noise, and reliability of the compression mechanism 300 for three cases of the discharge valve sheet 8 having different rigidity, the presence or absence of the transmission member, and different refrigerants as follows.

Wherein the displacement of the compression mechanism 300 is 10 cm < 3 >, the inner diameter of the cylinder 1 is 43 mm, the eccentricity of the crankshaft 4 is 4.25 mm, the diameter of the exhaust hole 2 is 6.5 mm, the refrigerant is R290 and R32 respectively, and the displacement of the compressor is divided by the rigidity V of the exhaust valve plate 8_sum/K_sum26000 mm4/N, 38000 mm4/N, 50000mm4/N, 80000 mm4/N, 130000 mm4/N, 200000 mm4/N, 350000 mm4/N, 450000 mm4/N, respectively.

R290 represents a refrigerant having a low discharge density, and R32 represents a refrigerant having a high discharge density.

(1) The energy efficiency results of the refrigeration device under the national standard working conditions, which are shown in tables 1 and 2, were obtained by using R290 refrigerant and R32 refrigerant, respectively.

Table 1: energy efficiency comparison table under national standard working condition of refrigerating device by adopting R290 refrigerant

As shown in Table 1, the energy efficiency of the compression mechanism 300 at 30 rpm without transmission components is V with R290 refrigerant_sum/K_sumAt least 80000 mm4/N, the efficiency is seriously deteriorated when the rotating speed is 90 rpm/s. In the presence of a transmission member, at V_sum/K_sumWhen the speed is more than or equal to 80000 mm 4/Newton, the energy efficiency is good at each rotating speed, and when the rigidity of the exhaust valve plate 8 is increased, V is_sum/K_sumWhen the ratio of (A) is reduced, the energy efficiency is obviously deteriorated when the rotating speed is 30R/s, so that for adopting R290 refrigerant, V is less than or equal to V at 80000 mm4/N_sum/K_sumThe compression mechanism 300 is energy efficient at up to 450000 mm 4/N.

Table 2: energy efficiency comparison table adopting R32 refrigerant under national standard working condition of refrigerating device

As shown in Table 2, with the R32 refrigerant, the energy efficiency of the compression mechanism 300 at the rotation speed of 30R/s is deteriorated without transmission parts, and is advanced to 38000 mm4/N, and even the exhaust valve plate 8 is broken at 450000 mm4/N, at which time the energy efficiency of the compression mechanism 300 at 30R/s is 50000mm4/N V_sum/K_sumAt most 350000 mm 4/cow, V_sum/K_sumThe deterioration occurred at 450000 mm 4/cow.

Has a transmission part and V is less than or equal to V at 50000mm4/N_sum/K_sumAt 350000 mm4/N or less, the energy efficiency of the compression mechanism 300 at each rotation speed is good, and when the rigidity of the exhaust valve plate 8 is increased, i.e., V_sum/K_sumWhen the ratio of (A) is decreased, the energy efficiency deteriorates at a rotation speed of 30 rpm, and when the rigidity of the exhaust valve sheet 8 is decreased, i.e., V_sum/K_sumWhen the ratio of (a) is increased, the energy efficiency is not further improved at the rotation speed of 30 rpm but rather deteriorated, and the degree of deterioration is more remarkable than that at the rotation speed of 90 rpm, because the rigidity of the discharge valve sheet 8 is too low,the surface of the exhaust valve plate 8 is sunken or deformed, so that the exhaust valve plate 8 closes the exhaust hole 2 loosely, and extra leakage loss is generated to reduce energy efficiency. At low speeds, leakage is more pronounced, so for R32 refrigerant, the compression mechanism 300 is at 50000mm4/N V_sum/K_sumThe energy efficiency is good when the concentration is less than or equal to 350000 mm and 4/cattle.

(2) The results of the noise (dB) comparison experiment of the compression mechanism 300 were obtained using R290 refrigerant and R32 refrigerant, respectively, at a rotation speed of 90 revolutions per second, as shown in table 3.

Table 3: noise comparison test table at 90 rpm using R290/R32 refrigerant

As shown in Table 3, V was calculated using R290 refrigerant without transmission member_sum/K_sumWhen the speed is more than or equal to 50000mm4/N, the noise of the exhaust valve plate 8 is deteriorated, and the performance deterioration is consistent with the performance deterioration of the non-transmission part at the rotating speed of 90 revolutions per second. When the transmission part is arranged, the noise of the exhaust valve plate 8 under each rigidity is normal. For the R32 refrigerant, the noise occurrence worsens at V_sum/K_sumNot less than 38000 mm4/N, which is consistent with the performance deterioration of 90 rpm/s without transmission part, and with transmission part, the compression mechanism 300 is only V_sum/K_sumThe noise is slightly worsened at 450000 mm 4/n.

(3) Using R290 refrigerant and R32 refrigerant, respectively, reliability results for the discharge valve plate 8 were obtained for 500 hours of continuous operation at different rotational speeds (rpm) as shown in tables 4 and 5.

Table 4: exhaust valve plate reliability comparison table adopting R290 refrigerant to continuously operate for 500H at different rotating speeds (revolutions per second)

As shown in Table 4, for the refrigerant using R290, V was measured without a transmission member_sum/K_sumWhen the rigidity of the exhaust valve plate 8 is more than or equal to 50000mm 4/ox, the reliability of the exhaust valve plate does not reach the standard, and the rigidity V is ultralow_sum/K_sumAt 450000 mm4/N, the exhaust valve plate 8 is broken after operating for 14 hours at the rotating speed of 110 rpm; v is more than or equal to 26000 mm4/N under the condition of a transmission component_sum/K_sumWhen the air flow is less than or equal to 350000 mm4/N, the reliability of the air exhaust valve plate 8 is not problem.

Table 5: discharge valve sheet reliability result table for 500 hours of continuous operation under different rotating speeds (revolutions per second) of R32 refrigerant

As shown in Table 5, for the refrigerant R32, V was measured without transmission member_sum/K_sumWhen the air outlet valve plate 8 has the same rigidity, the breaking time of the air outlet valve plate 8 is faster than that of the air outlet valve plate 8 adopting R290 refrigerant; v is more than or equal to 26000 mm4/N under the transmission component_sum/K_sumUnder the condition that the air outlet valve plate is less than or equal to 200000 mm 4/ox, the reliability of the air outlet valve plate 8 is high.

In conclusion, the inventor researches three influencing factors of energy efficiency, noise and reliability results to obtain the following results.

When the refrigerant with low exhaust density such as R134a or R290 is adopted, V is used for ensuring low noise and reliability under the condition of no transmission component_sum/K_sumIs required to be controlled at V_sum/K_sumLess than or equal to 38000 mm4/N, wherein the energy efficiency is 303.2% at a rotation speed of 30 rpm. With transmission members, V_sum/K_sumThe range of (A) needs to be controlled to be V less than or equal to 80000 mm4/N_sum/K_sumLess than or equal to 350000 mm 4/cow, wherein the highest energy efficiency is 307.1% when the rotating speed is 30 r/s, and the energy efficiency is obviously improved.

When the refrigerant with low exhaust density such as R134a or R290 is adopted, namely the refrigerant with high exhaust density such as R32 is adopted, V is realized without a transmission part_sum/K_sumIs required to be controlled at V_sum/K_sum26000 mm4/N, wherein the energy efficiency is 294.2% when the rotating speed is 30 r/s. With transmission members, V_sum/K_sumThe range of (B) needs to be controlled to be 50000mm4/N ≦ V_sum/K_sumIs less than or equal to 200000 mm 4/cow, wherein the highest energy efficiency is 297.1% when the rotating speed is 30 revolutions per second, and the energy efficiency is obviously improved.

Preferably, the sum V of the volumes of the plurality of cylinder chambers 101_sumHas a value in the range of 5000 mm 3-V_sum16000 mm 3, the energy efficiency of the compression mechanism 300 is higher.

In some embodiments, as shown in fig. 7 and 8, the exhaust valve sheet 8 is a reed valve sheet, the exhaust valve sheet 8 includes a fixed end 801, a free end 802, and a waist 803 located between the fixed end 801 and the free end 802, and the fixed end 801 of the exhaust valve sheet 8 is provided with a first mounting hole 8011. The projection area of the exhaust hole 2 on the free end 802 of the exhaust valve plate 8 is set as the windward area 804 of the exhaust valve plate 8, and the contact position of the transmission part when contacting the exhaust valve plate 8 is located in the windward area 804. The contact position of the transmission part and the exhaust valve block 8 is located in the windward area 804, when the transmission part presses the exhaust valve block 8 to close the exhaust hole 2, the exhaust hole 2 is closed stably, the exhaust valve block 8 is not easy to rebound or warp when the exhaust hole 2 is closed, and the closeness of the exhaust hole 2 is improved.

In some embodiments, as shown in fig. 7 and 8, the compression mechanism 300 further includes a lift stopper 9 for limiting the lift of the exhaust valve sheet 8, the lift stopper 9 is disposed on the exhaust valve sheet 8, the lift stopper 9 includes a horizontal section 901 and a curved section 902, the horizontal section 901 is provided with a second mounting hole 9011, the exhaust valve sheet 8 and the lift stopper 9 are mounted together by a fastener 5011 passing through the first mounting hole 8011 and the second mounting hole 9011, and the fastener 5011 may fix the exhaust valve sheet 8 and the lift stopper 9 on the upper bearing 5 by using a screw, a bolt, a rivet, or the like. Specifically, the upper surface of the upper bearing 5 is provided with a receiving groove 501, and the exhaust valve sheet 8 and the lift stopper 9 are mounted at the bottom of the receiving groove 501 by a fastener 5011. The bent section 902 of the lift limiter 9 is provided with an avoiding hole 9021 for avoiding a transmission component, and the transmission component can pass through the avoiding hole 9021 to be in contact with the free end 802 of the exhaust valve plate 8 so as to drive the exhaust valve plate 8. It is to be understood that the relief holes 9021 may be circumferentially open holes as shown in fig. 2, or may be closed holes as shown in fig. 13. The specific form of the avoiding hole 9021 can be designed according to the specific form of the transmission component, so that the purpose of not interfering with the transmission component is achieved.

In some embodiments, as shown in fig. 7A and 7B, the distance from the center of the exhaust hole 2 to the center of the first mounting hole 8011 is L mm, and the distance from the center of the second mounting hole 9011 to the intersection of the curved segment 902 and the horizontal segment 901 is L1 mm; as shown in fig. 8A and 8B, the width of the waist 803 of the vent valve sheet 8 is B mm, the thickness of the vent valve sheet 8 is T mm, the elastic modulus of the vent valve sheet 8 is E n/mm 2, and the stiffness of the vent valve sheet 8 is K n/mm, wherein:

therefore, the rigidity of the exhaust valve plate 8 can be further optimized according to the cantilever beam theory, so that the reliability of the exhaust valve plate 8 in working is improved.

Preferably, the thickness T of the discharge valve sheet 8 and the distance L from the center of the discharge hole 2 to the first mounting hole 8011 satisfy the relation: L/T is more than or equal to 120 and less than or equal to 200. Further, the thickness T of the exhaust valve sheet 8 and the width B of the waist 803 satisfy the relation: t is more than or equal to 0.3 mm 2 and less than or equal to 0.8 mm 2, so that the working strength of the exhaust valve plate 8 is ensured, and the reliability of the exhaust valve plate 8 in working is improved.

In some embodiments, the cylinder chamber 101 is a cavity of a cylindrical structure, the diameter of the cylinder chamber 101 is d1, and the exhaust hole 2 is a cylindrical hole with a uniform cross section; the piston 3 is of cylindrical structure, the diameter of the piston 3 is d2, the height of the cylinder chamber 101 is h, and the working chamber volume of the cylinder chamber 101 is V, wherein

In the embodiment of the present invention, the transmission member drives the discharge valve plate 8 to close the discharge hole 2 when the sliding piece 7 moves outward, which should be broadly understood as follows.

In some embodiments, the transmission part contacts the discharge valve plate 8 to drive the discharge valve plate 8 to close the discharge hole 2 after the sliding plate 7 moves outwards from the inner limit position by a predetermined distance. In other words, before the sliding piece 7 moves from the inner limit position to the outer limit position by the predetermined distance, the transmission part moves towards the exhaust valve sheet 8, but does not contact with the exhaust valve sheet 8, and does not drive the exhaust valve sheet 8, and after the sliding piece 7 moves by the predetermined distance, the transmission part contacts with the exhaust valve sheet 8 and drives the exhaust valve sheet 8 to move towards the exhaust hole 2 to close the exhaust hole 2.

In other embodiments, the transmission member is in contact with the discharge valve plate 8 when the slide 7 is in the inner limit position. In other words, when the sliding vane 7 is at the inner limit position, the transmission part is in contact with the exhaust valve sheet 8, and in the process that the sliding vane 7 moves from the inner limit position to the outer limit position, the transmission part drives the exhaust valve sheet 8 to move towards the exhaust hole 2 so as to gradually close the exhaust hole 2. Because when the gleitbretter 7 outwards moved, transmission unit contacts with discharge valve piece 8 all the time, can slow down the instantaneous speed that discharge valve piece 8 closed exhaust hole 2, reduces the noise that the discharge valve piece 8 struck the disk seat and produced when closing exhaust hole 2.

In some embodiments, the upper bearing 5 is provided above the cylinder 1 to close the upper end of the cylinder chamber 101, the lower bearing 6 is located below the cylinder 1 to close the lower end of the cylinder chamber 101, and the exhaust hole 2 is formed on at least one of the upper bearing 5 and the lower bearing 6. As shown in fig. 2 and 4 to 5, the discharge hole 2 is formed on the upper bearing 5, i.e., the discharge hole 2 penetrates the upper bearing 5 and communicates with the cylinder chamber 101. It is understood that the exhaust holes 2 may be formed on the lower bearing 6, or both the upper bearing 5 and the lower bearing 6. It will be appreciated that the discharge holes 2 may be formed at other positions, for example, in the embodiment of the multi-cylinder compressor, the discharge holes 2 may be formed on the partition plate between the adjacent cylinders 1.

In some embodiments, as shown in fig. 9 and 10, the transmission member is a swinging member, in particular, the transmission member is a swinging rod 10, and the swinging rod 10 is swingable about a pivot 11 mounted on the upper bearing 5. When the slide sheet 7 moves outwards, the swing rod 10 is driven to swing around the pivot 11, for example, in fig. 9 and 10, the swing rod 10 swings anticlockwise, so as to drive the exhaust valve sheet 8 to close the exhaust hole 2 downwards.

As shown in fig. 2, fig. 4-6 and fig. 9-10, the swing link 10 includes a lever 1001, a slide contact 1002 and a valve plate contact 1003. The pivot 11 is pivotally supported at the middle of the lever 1001, and the vane contact portion 1002 and the valve sheet contact portion 1003 are respectively located at both ends of the lever 1001. For example, the valve plate contact portion 1003 is disposed at a first end (left end in fig. 6) of the rod 1001, that is, one end of the rod 1001 close to the exhaust valve plate 8 when the exhaust valve plate 8 is closed, and the slide plate contact portion 1002 is disposed at a second end (right end in fig. 6) of the rod 1001, that is, one end of the rod 1001 close to the outer end of the slide plate 7 when the exhaust valve plate 8 is closed. When the sliding sheet 7 moves outward, the outer end of the sliding sheet 7 drives the sliding sheet contact portion 1002, so that the rod 1001 swings counterclockwise around the pivot 11, the valve sheet contact portion 1003 moves toward the exhaust hole 2, and the exhaust valve sheet 8 is pushed to close the exhaust hole 2.

As described above, the valve sheet contact part 1003 may contact the exhaust valve sheet 8 after the sliding sheet 7 moves backward from the inner limit position by a predetermined distance, that is, after the rod 1001 swings counterclockwise by a predetermined angle, the valve sheet contact part 1003 contacts the exhaust valve sheet 8, and as the sliding sheet 7 continues to move outward, the rod 1001 continues to swing counterclockwise, and the valve sheet contact part 1003 drives the exhaust valve sheet 8 to move downward to close the exhaust hole 2. Alternatively, when the slide plate 7 is at the inner limit position, the valve plate contact portion 1003 is in contact with the vent valve plate 8, and when the slide plate 7 moves outward from the inner limit position, the valve plate contact portion 1003 pushes the vent valve plate 8 to gradually move downward to gradually close the vent hole 2.

In some embodiments, as shown in fig. 6 and 9 to 10, the valve sheet contact part 1003 extends from the rod 1001 toward a side of the discharge hole 2. Preferably, the valve sheet contact 1003 is perpendicular to the rod 1001, the slide sheet contact 1002 and the valve sheet contact 1003 are integrally formed with the rod 1001, and the valve sheet contact 1003 may be fixed to the rod 1001 by welding, screwing, or the like. In the embodiment shown in FIGS. 9 and 10, slider contact 1002 is formed by the second end of rod 1001 or a portion thereof.

In some embodiments, the slider contact 1002 is in constant contact with the slider 7, e.g., the outer end of the slider 7. In other words, when the slide 7 reciprocates between the inner limit position and the outer limit position, the slide contact portion 1002 is always in contact with and does not separate from the outer end of the slide 7. In some specific examples, the sliding piece contact portion 1002 can be always abutted to the outer end of the sliding piece 7 by an elastic member, for example, a compression spring or a leaf spring is disposed between the swing rod 10 and the upper bearing 5, or a torsion spring is disposed on the pivot 11, so that the sliding piece 7 is prevented from being collided with the sliding piece contact portion 1002 during movement, noise generated during operation of the compression mechanism 300 is reduced, and the service life of the transmission component and the swing rod 10 is prolonged.

In some embodiments, as shown in fig. 7A and 7B, the lift limiter 9 is disposed above the exhaust valve sheet 8. When the valve sheet contact portion 1003 moves downward, the valve sheet contact portion 1003 passes through the avoiding hole 9021 to contact the exhaust valve sheet 8, so that the swing rod 10 does not interfere with the lift stopper 9, and in this embodiment, the avoiding hole 9021 is a hole with a circumferential opening.

In some embodiments, as shown in FIGS. 3 to 5, it is preferable that, in order to make the swing link 10 move smoothly, the degrees of freedom of the swing link 10 in other directions are restricted except for the degree of freedom of swing, and the restriction gap is ≦ 0.05 mm. For example, to limit the displacement of the rocker 10 in the axial direction of the pivot 11, the rocker 10 is supported by the pivot 11 to swing in a groove formed in the upper bearing 5, the groove width is b, and the transmission member width b1 satisfies the relation: b-b1 is more than 0 and less than or equal to 0.05 mm. To limit the displacement of the rocker 10 in the radial direction of the pivot 11, the diameter d2 of the pivot 11 hole 1004 on the upper bearing 5, the diameter d1 of the pivot 11 hole 1004 of the transmission component and the diameter d of the pivot 11 satisfy the following relation: d1-d is less than or equal to 0.05 mm and d2-d is less than or equal to 0.05 mm, so that the running stability of the compression mechanism 300 is improved.

In other embodiments, as shown in fig. 13 to 17, the transmission member is a translation member 12. The transmission component comprises a main translational member 1201 and an auxiliary translational member 1202, when the slide sheet 7 moves outwards, the main translational member 1201 is driven to translate, for example, to translate leftwards in fig. 15-17, and the main translational member 1201 drives the auxiliary translational member 1202 to translate, for example, to translate downwards in fig. 15-17, so as to drive the exhaust valve sheet 8 to close the exhaust hole 2.

Specifically, as shown in fig. 18, the main translational member 1201 includes a first vertical segment 12011, a first horizontal segment 12012, a second vertical segment 12013, a second horizontal segment 12014, and an inclined segment 12015, wherein an upper end of the first vertical segment 12011 is connected to a right end of the first horizontal segment 12012, and preferably has an arc transition, a lower end of the second vertical segment 12013 is connected to a left end of the first horizontal segment 12012, a right end of the second horizontal segment 12014 is connected to an upper end of the second vertical segment 12013, and the inclined segment 12015 is connected to a left end of the second horizontal segment 12014, it should be understood that the inclined segment 12015 may be inclined or curved. The lower surface of the inclined section 12015 forms a guide surface 12016, and the guide surface 12016 may be a shoe upper or a curved surface. The end of the primary translational member 1201 remote from the secondary translational member 1202 is connected to the outer end face of the sliding piece 7, and as shown in fig. 15-17, the first vertical section 12011 is connected to the outer end face of the sliding piece 7. In some embodiments, secondary translational member 1202 is cylindrical and has a hemispherical upper end.

When the sliding sheet 7 moves outwards, the main translational member 1201 is driven to translate outwards (rightwards in fig. 15-17), and the guide surface 12016 of the main translational member 1201 is in contact with the secondary translational member 1202 to drive the secondary translational member 1202 to move downwards, so that the exhaust valve sheet 8 is driven to close the exhaust hole 2. When the sliding sheet 7 moves outwards, the outer end of the sliding sheet 7 pushes the main translational member 1201 to translate rightwards, and under the guiding action of the guide surface 12016 of the main translational member 1201, the main translational member 1201 pushes the auxiliary translational member 1202 to move towards the exhaust hole 2 (downwards in fig. 15-17), so that the exhaust valve sheet 8 is driven to close the exhaust hole 2.

In some embodiments, the main translational member 1201 and the sliding vane 7 may be in contact with each other all the time and may not be separated from each other, thereby preventing the sliding vane 7 from colliding with the main translational member 1201 during movement, reducing noise, and prolonging the service life of the transmission component and the sliding vane 7.

In some embodiments, after the sliding plate 7 moves outward from the inner limit position for a certain distance, the secondary translational member 1202 contacts the air release flap 8, and drives the flap contact portion 1003 to close the air release flap 8.

Alternatively, when the sliding vane 7 is in the inner limit position, the secondary translational member 1202 contacts the guide surface 12016 and the discharge valve plate 8, so that when the sliding vane 7 starts to move outwards from the inner limit position, the secondary translational member 1202 immediately drives the discharge valve plate 8 to move towards the discharge hole 2 to close the discharge hole 2. Therefore, the auxiliary translation piece 1202 is always in contact with the guide surface 12016 and the exhaust valve plate 8, the instantaneous speed of the exhaust valve plate 8 for closing the exhaust hole 2 can be reduced, and the noise generated when the exhaust valve plate 8 closes the exhaust hole 2 is further reduced.

Optionally, when the slide 7 is in the inner limit position, the secondary translational member 1202 is in contact with the lower surface of the second horizontal segment 12014 of the primary translational member 1201, only after the primary translational member 1201 translates to the right by a predetermined distance, however, the secondary translational member 1202 contacts the guide surface 12016, when the sliding sheet 7 moves outwards from the inner extreme position, the main translational member 1201 is driven to move outwards, and at the moment, the upper end of the auxiliary translational member 1202 is in contact with the lower surface of the second horizontal segment 12014 of the main translational member 1201, so that the auxiliary translational member 1202 does not move downwards, after the sliding piece 7 and the main translational member 1201 move outwards for a preset distance, the upper end of the secondary translational member 1202 starts to contact with the guide surface 12016, so that the guide surface 12016 drives the secondary translational member 1202 to move downwards, in this case, the sub-translation member 1202 may contact the discharge valve sheet 8 to drive the discharge valve sheet 8 immediately when contacting the guide surface 12016, or may contact the discharge valve sheet 8 to drive the discharge valve sheet 8 after moving downward by a predetermined distance.

In some embodiments, the lift stopper 9 is disposed above the exhaust valve plate 8, the avoidance hole 9021 is a circumferentially closed hole, and the secondary translational member 1202 can pass through the avoidance hole 9021 to reciprocate in the axial direction of the avoidance hole 9021, so that the avoidance hole 9021 functions to guide the secondary translational member 1202.

In some embodiments, it is preferable that, in order to make the translational part 12 move smoothly, all spatial degrees of freedom are constrained except the translational degree of freedom of the translational part 12, and the constraint gap is less than or equal to 0.05 mm.

The following describes the compression mechanism 300 according to some specific examples of the present invention with reference to the drawings.

As shown in fig. 1 to 12, a compression mechanism 300 according to an embodiment of the present invention includes a cylinder 1, a piston 3, a crankshaft 4, an upper bearing 5, a lower bearing 6, a vane 7, an exhaust valve sheet 8, a lift stopper 9, and a rocker 10. The cylinder 1 is provided with a cylinder chamber 101, the upper bearing 5 and the lower bearing 6 are respectively arranged on the upper surface and the lower surface of the cylinder 1 to seal the cylinder chamber 101 of the cylinder 1, the piston 3 is arranged in the cylinder chamber 101, one end of the crankshaft 4 is provided with an eccentric part 401, the piston 3 is sleeved on the eccentric part 401, and the crankshaft 4 drives the piston 3 to eccentrically rotate in the cylinder chamber 101.

A slide sheet groove 102 is arranged in the cylinder 1, and the inner end of the slide sheet groove 102 is communicated with the cylinder chamber 101. The inner end of the slide 7 abuts on the piston 3, and the slide 7 is reciprocally movable between an inner limit position and an outer limit position in the slide groove 102. The upper surface of upper bearing 5 is provided with holding tank 501, and exhaust hole 2 has been seted up to the tank bottom of holding tank 501, and exhaust hole 2 communicates with jar room 101. The exhaust valve plate 8 and the lift limiter 9 are arranged in the accommodating groove 501, the lift limiter 9 is located above the exhaust valve plate 8, the exhaust valve plate 8 is a reed valve plate with elasticity, the fixed end 801 of the exhaust valve plate 8 is fixed at the bottom of the accommodating groove 501, and the free end 802 is used for opening and closing the exhaust hole 2. The lift limiter 9 is provided with an avoidance hole 9021 for avoiding the swing rod 10.

The pendulum rod 10 is swingable about a pivot 11 mounted on the upper bearing 5. The swing link 10 includes a link 1001, a slide contact 1002, and a valve plate contact 1003. The rod 1001, the slide contact 1002 and the valve plate contact 1003 are integrated. The pivot 11 is supported at the middle of the rod 1001, and the slide contact 1002 is disposed at an end of the rod 1001 corresponding to the slide 7, for example, formed by an end of the rod 1001 or a portion of an end of the rod 1001. The valve sheet contact portion 1003 is disposed at the other end of the rod 1001 and is substantially perpendicular to the rod 1001. The sheet contact part 1003 may be cylindrical and have a hemispherical lower end.

The swing rod 10 is linked with the sliding sheet 7, when the sliding sheet 7 moves outwards, the outer end of the sliding sheet 7 drives the sliding sheet contact part 1002, so that the rod body 1001 swings around the pivot 11, the valve sheet contact part 1003 moves towards the exhaust hole 2, and the exhaust valve sheet 8 is pushed to close the exhaust hole 2.

When the exhaust valve plate 8 closes the exhaust hole 2, the projection area of the exhaust hole 2 on the exhaust valve plate 8 is a windward area 804, and the contact position of the valve plate contact part 1003 and the exhaust valve plate 8 is located in the windward area 804. The lower end of the slider contact 1002 may be provided with a wear resistant or resilient material layer. A torsion spring may be mounted in the pivot 11 so that the slider contact 1002 is always in contact with the slider 7.

The operation of the compression mechanism 300 according to some specific examples of the present invention is described below.

As shown in fig. 9 and 12, when the crank angle is 180 degrees, the slide plate 7 moves to the inner limit position, the exhaust valve plate 8 does not close the exhaust hole 2 and allows the exhaust through the exhaust hole 2, and the plate contact portion 1003 of the swing lever 10 does not contact the exhaust valve plate 8. When the piston 3 continues to rotate from the 180-degree rotation angle, that is, the slide plate 7 moves from the inner limit position shown in fig. 12 to the outer limit position shown in fig. 11, the slide plate 7 drives the swing rod 10 to swing counterclockwise from the position shown in fig. 9, the valve plate contact portion 1003 contacts the exhaust valve plate 8 and drives the exhaust valve plate 8 downwards to gradually close the exhaust hole 2, and finally, the slide plate 7 moves to the outer limit position shown in fig. 11, and the valve plate contact portion 1003 of the swing rod 10 drives the exhaust valve plate 8 to completely close the exhaust hole 2.

As shown in fig. 13 to 17, a compression mechanism 300 according to other specific examples of the present invention includes a cylinder 1, a piston 3, a crankshaft 4, an upper bearing 5, and a lower bearing 6. The cylinder 1 has a cylinder chamber 101 therein, the upper bearing 5 and the lower bearing 6 are respectively mounted on the upper and lower ends of the cylinder 1 to close the cylinder chamber 101 of the cylinder 1, the piston 3 is mounted inside the cylinder chamber 101, one end of the crankshaft 4 is provided with an eccentric portion 401, the piston 3 is sleeved on the eccentric portion 401, and the crankshaft 4 drives the piston 3 to eccentrically rotate in the cylinder chamber 101.

A slide groove 102 is provided in the cylinder 1, and one end of the slide groove 102 communicates with the cylinder chamber 101. The slide sheet 7 is arranged in the slide sheet groove 102, the slide sheet 7 can move back and forth between an inner limit position and an outer limit position, and the inner end of the slide sheet 7 is abutted to the piston 3. The upper surface of upper bearing 5 is provided with holding tank 501, and exhaust hole 2 has been seted up to the tank bottom of holding tank 501, and exhaust hole 2 communicates with jar room 101. The accommodating groove 501 is also internally provided with an exhaust valve plate 8 and a lift limiter 9, the lift limiter 9 is arranged on the exhaust valve plate 8, the exhaust valve plate 8 is a reed valve plate with elasticity, one end of the exhaust valve plate 8 is a fixed end 801 fixed at the bottom of the accommodating groove 501, and the other end of the exhaust valve plate 8 is a free end 802 for opening and closing the exhaust hole 2. One end of the lift limiter 9 is provided with an avoidance hole 9021.

The compression mechanism 300 further comprises a translational member 12, and the translational member 12 comprises a primary translational member 1201 and a secondary translational member 1202. The translational part 12 is linked with the slide 7. Specifically, when the slide sheet 7 moves outwards, the main translation member 1201 is driven to translate outwards, and the main translation member 1201 drives the auxiliary translation member 1202 to translate downwards so as to drive the exhaust valve sheet 8 to close the exhaust hole 2.

In particular, the main translational member 1201 forms a generally ladder-like structure and includes a first vertical segment 12011, a first horizontal segment 12012, the upper end of the first vertical section 12011 is connected with the right end of the first horizontal section 12012, preferably in arc transition, the lower end of the second vertical section 12013 is connected with the left end of the first horizontal section 12012, the right end of the second horizontal section 12014 is connected with the upper end of the second vertical section 12013, the inclined section 12015 is connected with the left end of the second horizontal section 12014, the first vertical section 12011 extends vertically downwards and abuts against the sliding sheet 7, the lower surface of the inclined section 12015 forms a guide surface 12016 which is inclined inwards downwards or in an arc shape, the upper end of the secondary translation piece 1202 is of a curved surface structure and is used for abutting against the guide surface 12016, and the secondary translation piece 1202 is matched in the avoiding hole 9021 and can move back and forth along the axial direction of the avoiding hole 9021. When the sliding sheet 7 moves outwards, the outer end of the sliding sheet 7 pushes the first vertical section 12011 to move outwards, and then the auxiliary translation member 1202 is pushed to move downwards through the guide surface 12016, so that the exhaust valve sheet 8 is driven to close the exhaust hole 2. The operation of the compression mechanism 300 according to other specific examples of the present invention will be described below.

As shown in fig. 12 and 16, when the crank angle is 180 degrees, the slide plate 7 moves to the inner limit position, the discharge valve plate 8 does not close the discharge hole 2 and allows discharge through the discharge hole 2, and the upper end of the secondary translational member 1202 does not contact the guide surface 12016 of the primary translational member 1201. When the piston 3 continues to rotate from a 180-degree angle, namely the sliding piece 7 moves from the inner limit position shown in fig. 12 to the outer limit position shown in fig. 11, the main translational piece of the sliding piece 7 translates from the position shown in fig. 16 to the position shown in fig. 17, the upper end of the auxiliary translational piece 1202 is in contact with the guide surface 12016, the auxiliary translational piece 1202 is driven to translate downwards, so that the exhaust valve plate 8 is driven to close the exhaust hole 2 gradually, and finally, the sliding piece 7 moves to the outer limit position shown in fig. 11, and the auxiliary translational piece 1202 drives the exhaust valve plate 8 to close the exhaust hole 2 completely.

In some embodiments, the rotary compressor may be a multi-cylinder compressor, and the rotary compressor may be a fixed speed compressor or a variable speed compressor.

In some embodiments, the maximum operating speed of the rotary compressor is greater than 150 revolutions per second and less than 240 revolutions per second. The rotary compressor implemented by the invention has more obvious effect in high-speed operation, for example, the rigidity of the exhaust valve plate 8 can be freely and flexibly designed, the timeliness and the reliability of closing the exhaust valve plate 8 are ensured, the exhaust valve plate 8 is easy to open, the exhaust resistance loss is small, and the exhaust noise is reduced.

The refrigeration device according to the embodiment of the invention comprises the rotary compressor according to the embodiment of the invention.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. 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 present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the present disclosure, the terms "one embodiment," "some embodiments," "an example," "a specific example," or "some examples" and the like mean that a specific feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the terms used above are not necessarily intended to 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. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. A compression mechanism, comprising:

the air cylinder comprises at least one air cylinder, wherein each air cylinder is internally provided with a cylinder chamber and a slide sheet groove, a piston is arranged in the cylinder chamber, a slide sheet is arranged in the slide sheet groove, the inner end of the slide sheet is abutted against the piston, the slide sheet can reciprocate between an inner limit position and an outer limit position, the cylinder chamber is provided with an exhaust hole communicated with the cylinder chamber, and an exhaust valve plate is configured on the exhaust hole and used for opening and closing the exhaust hole;

a crankshaft for driving the piston to eccentrically rotate within the cylinder chamber to compress refrigerant;

an upper bearing and a lower bearing rotatably supporting the crankshaft, the upper bearing closing an upper end of the cylinder chamber, the lower bearing closing a lower end of the cylinder chamber;

the transmission component drives the exhaust valve plates to close the exhaust holes when the sliding sheet moves outwards, wherein the rigidity of each exhaust valve plate is K, the unit is N/mm, when K is equal to the projection point of the central axis of each exhaust hole on the exhaust valve plates in the numerical value and rises by 1 mm, the force needs to be applied to the projection point along the central axis of each exhaust hole, and the sum of the volumes of the cylinder chambers is V_sumMillimeter³Sum of stiffness K of the exhaust valve sheet_sumWherein the following relationship is satisfied:

when the refrigerant is R134a or R290, 80000 mm⁴V is less than or equal to ox_sum/K_sumLess than or equal to 350000 mm⁴A/cow;

when the refrigerant is other than R134a or R290, 50000mm⁴V is less than or equal to ox_sum/K_sumLess than or equal to 200000 mm⁴A/cattle.

2. The compression mechanism of claim 1, wherein: 5000 mm³≤V_sumLess than or equal to 16000 mm³。

3. The compressing mechanism as claimed in claim 1, further comprising a lift stopper for limiting the lift of the discharge valve plate, wherein the discharge valve plate includes a fixed end, a free end and a waist portion located between the fixed end and the free end, the fixed end of the discharge valve plate is provided with a first mounting hole, the lift stopper is provided on the discharge valve plate and includes a horizontal section and a curved section, the horizontal section is provided with a second mounting hole, the discharge valve plate and the lift stopper are mounted together by a fastener passing through the first mounting hole and the second mounting hole, the distance from the center of the discharge hole to the center of the first mounting hole is L mm, the distance from the center of the second mounting hole to the junction of the curved section and the horizontal section is L1 mm, the width of the waist portion is B mm, and the thickness of the discharge valve plate is T mm, the elastic modulus of the exhaust valve plate is E N/mm²The rigidity of the exhaust valve plate is K newtons per millimeter, wherein:

4. the compression mechanism of claim 3, wherein 120 ≦ L/T ≦ 200.

5. A compression mechanism as claimed in claim 3, wherein 0.3 mm²T multiplied by B is less than or equal to 0.8 mm²。

6. The compression mechanism of any one of claims 1-5, wherein the cylinder chamber is cylindrical and has a diameter d1 cavity, the piston is cylindrical and has a diameter d2, the height of the cylinder chamber is h, and the working chamber volume is V, wherein

7. The compressing mechanism as claimed in claim 1, wherein the transmission member contacts the discharge valve plate when the slide is at the inner limit position or contacts the discharge valve plate after the slide moves outward from the inner limit position by a predetermined distance to drive the discharge valve plate to close the discharge hole.

8. The compressing mechanism as claimed in any one of claims 1 to 7, wherein the transmission member is a swing link, and the swing link is driven to swing around a pivot when the sliding piece moves outwards, so that the swing link drives the discharge valve plate to close the discharge hole.

9. The compressing mechanism as claimed in claim 8, wherein the swing link includes a rod, a sliding piece contact portion and a valve plate contact portion, and the sliding piece moves outward to drive the rod to swing by pushing the sliding piece contact portion, so that the valve plate contact portion drives the exhaust valve plate to close the exhaust hole.

10. The compression mechanism as claimed in any one of claims 1 to 7, wherein the transmission component includes a main translational member and an auxiliary translational member, the slide plate drives the main translational member to translate when moving outwards, and the main translational member drives the auxiliary translational member to translate so that the auxiliary translational member drives the exhaust valve plate to close the exhaust hole.

11. The compression mechanism as claimed in claim 10, wherein the primary translational member is provided with a guide surface for driving the secondary translational member, and the guide surface is a slope or an arc surface.

12. The compression mechanism as claimed in claim 11, wherein the secondary translational member contacts the guide surface when the slide is at or moves outwardly a predetermined distance from the inner limit position.

13. A rotary compressor characterized by comprising the compression mechanism according to any one of claims 1 to 12.

14. A refrigerating apparatus comprising the rotary compressor of claim 13.