CN111720314B

CN111720314B - Compression mechanism and compressor with same

Info

Publication number: CN111720314B
Application number: CN202010604991.XA
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: 2022-03-01
Anticipated expiration: 2040-06-29
Also published as: CN111720314A

Abstract

The invention discloses a compression mechanism and a compressor with the same. The compression mechanism includes: the air cylinder, the exhaust hole, the piston, the bent axle, upper bearing and lower bearing, gleitbretter, exhaust valve block, lift stopper and pendulum rod, the drive when gleitbretter outwards removes the pendulum rod is around the pivot swing so that the pendulum rod promotes the exhaust valve block is closed the exhaust hole, the pendulum rod have be used for with the valve block contact site of exhaust valve block contact and be used for with the gleitbretter contact site of gleitbretter contact, when valve block contact site protrusion lift stopper's spacing face, through the gleitbretter with the tangent line of the contact point of pendulum rod with the contained angle between the side of going up of gleitbretter is beta, and wherein beta is less than or equal to 10. According to the compression mechanism, the exhaust valve plate has the advantages of good applicability and reliability, low closing noise and high energy efficiency.

Description

Compression mechanism and compressor with same

Technical Field

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

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. 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.

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 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 realizes that the rigidity design problem of the exhaust valve sheet cannot be solved only by improving the structure and the material of the exhaust valve sheet, which results in the problem of poor 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 an 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 a cylinder, wherein a cylinder chamber and a slide sheet groove are arranged in the cylinder; an exhaust port in communication with the cylinder chamber; a piston; a crankshaft for driving the piston to eccentrically rotate within the cylinder chamber; an upper bearing and a lower bearing that rotatably support the crankshaft; the sliding sheet is arranged in the sliding sheet groove and can move back and forth between an inner limit position and an outer limit position, and the inner end of the sliding sheet is abutted against the piston; the exhaust valve plate is used for opening and closing the exhaust hole; the lift limiter is provided with a limiting surface used for limiting the lift of the exhaust valve plate; the pendulum rod, the gleitbretter drives when outwards moving the pendulum rod around the pivot swing so that the pendulum rod promotes the exhaust valve block is closed the exhaust hole, the pendulum rod have be used for with the valve block contact site of exhaust valve block contact with be used for with the gleitbretter contact site of gleitbretter contact, the gleitbretter have be used for with the pendulum rod contact site of pendulum rod contact, the surface of pendulum rod contact site is the curved surface the valve block contact site orientation the surface of exhaust hole with when spacing face parallel and level or tangent, on the central longitudinal section in gleitbretter groove, through the gleitbretter with the tangent line of the contact point of pendulum rod with the contained angle is beta between the side of going up of gleitbretter, wherein beta is less than or equal to 10.

According to the compression mechanism provided by the embodiment of the invention, when the sliding sheet moves from the inner limit position to the outer limit position, namely the sliding sheet moves along the center far away from the cylinder chamber, the swing rod applies closing force for closing the exhaust hole to the exhaust valve sheet, namely the exhaust valve sheet is driven to close the exhaust hole, the exhaust valve sheet is driven to close the exhaust hole by virtue of the driving force of the swing rod, 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 very small, the exhaust valve sheet is easy to open, the exhaust resistance loss is reduced, the design flexibility and applicability of the exhaust valve sheet are improved, the exhaust noise is reduced, and the swing rod is always in contact with the sliding sheet under the action of the elastic element, so that the sliding sheet cannot collide with the swing rod, and the noise is further reduced. Furthermore, when the contact part of the valve plate is flush or tangent with the limiting surface, the included angle beta between the tangent line of the contact point of the sliding sheet and the swing rod and the upper side surface of the sliding sheet is not more than 10 degrees, so that the speed of the contact part of the valve plate just protruding out of the limiting surface can be reduced, the impact speed of the valve plate contact part of the swing rod on the exhaust valve plate is further reduced, the abrasion degree of the valve plate contact part and the exhaust valve plate is reduced, and the working reliability of the compression mechanism is improved.

In some embodiments, β ≦ 5 ° for the maximum rotational speed of the piston of 150 rpm or greater.

In some embodiments, when the surface of the valve plate contact part facing the exhaust hole is flush with or tangent to the limiting surface to contact the exhaust valve plate, the crank angle is alpha, wherein alpha is greater than or equal to 280 degrees.

In some embodiments, the surface of the rocker contact is a circular arc.

In some embodiments, the rocker contact is a corner between an upper side surface of the slider and an outer end surface of the slider.

In some embodiments, a surface of at least one of the blade contact and the vane contact is coated with a wear resistant coating.

In some embodiments, a wear member is embedded in a surface of at least one of the blade contact portion and the vane contact portion.

In some embodiments, the swing rod contacts the exhaust valve plate after the slide sheet moves outwards from the inner limit position by a predetermined distance, so as to drive the exhaust valve plate to close the exhaust hole.

In some embodiments, the exhaust hole is formed on the upper bearing, and the exhaust valve plate is a reed valve plate and has a fixed end fixed on the upper bearing and a free end for opening and closing the exhaust hole.

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 diagram of a swing link according to an embodiment of the present invention.

Fig. 7A is a sectional view of a lift stopper of a compression mechanism according to an embodiment of the present invention.

FIG. 7B is a plan view of a lift stop of a compression mechanism according to an embodiment of the present invention.

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

Fig. 9 is a state view showing that the swing link of the compression mechanism does not contact the discharge valve sheet according to the embodiment of the present invention.

FIG. 10 is a diagram illustrating a state where a swing link of the compression mechanism is just in contact with the discharge valve sheet according to the embodiment of the present invention

FIG. 11 is a view illustrating a state in which a rocker lever of the compression mechanism closes the discharge valve sheet according to the embodiment of the present invention.

Fig. 12 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. 13 is a schematic view of a compression mechanism according to an embodiment of the present invention having a crank angle of 180 °.

FIG. 14 is a speed profile of a rocker lever at different beta values at crank angles in accordance with an 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;

6. a lower bearing;

7. sliding blades; 701. a swing link contact part;

8. an exhaust valve plate; 801. a fixed end; 802. a free end; 803. a fixing hole; 804. a windward region;

9. a lift limiter; 901. avoiding holes; 902. a limiting surface; 903. mounting holes;

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.

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 14.

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 14, 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, a lift stopper 9, and a rocker 10.

The cylinder 1 has a cylinder chamber 101 and a vane groove 102 therein. 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, 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. 13. 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. 12.

The discharge valve sheet 8 is used to open and close the discharge hole 2. The lift stopper 9 has a stopper surface 902 for restricting the lift of the exhaust valve sheet 8. The swing link 10 has a valve sheet contact portion 1003 for contacting the exhaust valve sheet 8 and a slide sheet contact portion 1002 for contacting the slide sheet 7, and the swing link 10 is used for driving the exhaust valve sheet 8 to close the exhaust hole 2 when the slide sheet 7 moves outwards. In other words, the swing link 10 is linked with the slide sheet 7, and when the slide sheet 7 moves from the inner limit position to the outer limit position, the slide sheet 7 drives the slide sheet contact portion 1002 of the swing link 10 to swing around the pivot 11, so that the sheet contact portion 1003 of the swing link 10 pushes the exhaust sheet 8 to close the exhaust hole 2. Further, the sliding vane 7 is provided with a swing lever contact part 701 for contacting with the swing lever 10, the surface of the swing lever contact part 701 is a curved surface, and when the surface of the valve plate contact part 1003 facing the exhaust hole 2 is flush with or tangent to the limiting surface 902, on the central longitudinal section of the sliding vane groove 102, an included angle β is formed between a tangent line passing through a contact point of the sliding vane 7 and the swing lever 10 and the upper side surface of the sliding vane 7, wherein β is less than or equal to 10 °, as shown in fig. 10.

As shown in fig. 1 to 5, when the compression mechanism 300 operates, the piston 3 eccentrically rotates in the cylinder chamber 101, the gas in the cylinder chamber 101 is compressed into high-pressure gas, when the pressure reaches a certain value, the gas pushes the exhaust valve plate 8 open and is exhausted from the exhaust hole 2, the piston 3 pushes the slide plate 7 to move from the inner limit position to the outer limit position, and the swing rod 10 applies a closing force to the exhaust valve plate 8 to close the exhaust hole 2, so as to drive the exhaust valve plate 8 to close the exhaust hole 2. Because the exhaust valve plate 8 is pushed by the swing rod 10 to close the exhaust hole 2, the timeliness and the reliability of closing the exhaust valve plate 8 are improved. Moreover, with the aid of the swing rod 10, the exhaust valve sheet 8 can be designed to have no rigidity (i.e. the exhaust valve sheet 8 is not fixed), so that the exhaust valve sheet 8 is easy to open, has a large opening degree, reduces exhaust resistance, reduces exhaust noise, and can ensure high energy efficiency at both high speed and low speed.

In addition, the surface of the swing link contact part 701 is of a curved surface structure, so that when the swing link contact part 701 pushes the slide sheet contact part 1002 to rotate around the pivot 11, the abrasion of the position of the swing link contact part 701 is reduced, and the working reliability of the compression mechanism 300 is improved. Further, when the surface of the valve sheet contact part 1003 facing the exhaust hole 2 is flush with or tangent to the limiting surface 902, an included angle β between a tangent line of a contact point of the sliding sheet 7 and the swing rod 10 and the upper side surface of the sliding sheet 7 is not more than 10 °. The speed of the valve plate contact part 1003 of the swing rod 10 just protruding out of the limiting surface 902 can be reduced, that is, the impact speed of the valve plate contact part 1003 of the swing rod 10 in contact with the exhaust valve plate 8 can be reduced, so that the abrasion degree of the valve plate contact part 1003 and the exhaust valve plate 8 is reduced, and the working reliability of the compression mechanism 300 is improved.

The inventor finds, through research, that the influence factors of the speed when the valve sheet contact part 1003 of the swing link 10 just protrudes from the limit surface 902 are as follows: the rotating speed of the piston 3, the eccentric amount of the crankshaft 4, the position of the center of the pivot 11, the crank angle when the valve sheet contact part 1003 of the swing rod 10 just protrudes out of the limit surface 902, and the included angle between the tangent of the contact point of the slide sheet 7 and the swing rod 10 when the swing rod 10 protrudes out of the limit surface 902 and the upper side surface of the slide sheet 7.

Since the rotational speed of the piston 3 and the eccentricity of the crankshaft 4 are generally constant values, they are not easily adjusted. The closer the distance from the center of the pivot 11 to the exhaust hole 2, the slower the swing speed of the swing lever 10, and the smaller the space for adjusting the position of the pivot 11 due to the space limitation of the compression mechanism 300. For the crank angle when the valve plate contact portion 1003 of the swing rod 10 just protrudes out of the limiting surface 902, the crank angle should not be too large or too small to ensure the performance of the compression mechanism 300, because when the crank angle is too small, the exhaust valve plate 8 is pressed by the swing rod 10 earlier to move downwards to close the exhaust valve, the flow area is small, the flow resistance loss is large, and the energy efficiency is low; when the compression rotation angle is too large, the swing rod 10 needs to press the exhaust valve plate 8 at a higher speed to ensure that the exhaust hole 2 is closed when the rotation angle of the crankshaft is 360 degrees, and the larger the pushing force of the slide sheet 7 on the swing rod 10 is, the larger the friction resistance loss is.

Therefore, when the valve sheet contact part 1003 of the swing rod 10 protrudes out of the limiting surface 902, the inventor controls an included angle β between a tangent line of a contact point of the slide sheet 7 and the swing rod 10 and an upper side surface of the slide sheet 7 to reduce the speed of the swing rod 10. Comparative experiments were performed as follows.

Specifically, the rotation speed of the piston 3 is 120 revolutions per second, the refrigerant is R32, the displacement is 10 cubic centimeters, the aperture of the exhaust hole 2 is 6.5 millimeters, the inner diameter of the cylinder 1 is 43 millimeters, the length of the sliding vane 7 is 21 millimeters, the eccentricity of the crankshaft 4 is 4.25 millimeters, the distance X from the axis of the pivot 11 to the center of the upper bearing 5 is 34.5 millimeters, the end surface Y of the upper bearing 5 is 2.9 millimeters, the distance L from the valve sheet contact part 1003 to the center of the pivot 11 is 15 millimeters, the crank angle when the valve sheet contact part 1003 of the swing link 10 just protrudes out of the limit surface 902 is 280 millimeters, and the arc radius of the swing link contact part 701 is R2.

The inventor finds out a speed curve diagram of different beta values under the crank angle through comparative experiments, as shown in fig. 14. And the following data results were obtained.

When the surface of the valve sheet contact part 1003 facing the exhaust hole 2 is flush with or tangent to the limit surface 902, on the central longitudinal section of the slide sheet groove 102, when an included angle beta between a tangent line passing through a contact point of the slide sheet 7 and the swing rod 10 and the upper side surface of the slide sheet 7 is 16 degrees, the speed of the valve sheet contact part 1003 protruding out of the limit surface 902 is 5.9 m/s.

When the surface of the valve sheet contact part 1003 facing the exhaust hole 2 is flush with or tangent to the limit surface 902, on the central longitudinal section of the slide sheet groove 102, when an included angle beta between a tangent line passing through a contact point of the slide sheet 7 and the swing rod 10 and the upper side surface of the slide sheet 7 is 10 degrees, the speed of the valve sheet contact part 1003 protruding out of the limit surface 902 is 3.2 m/s.

When the surface of the valve sheet contact part 1003 facing the exhaust hole 2 is flush with or tangent to the limit surface 902, on the central longitudinal section of the slide sheet groove 102, when an included angle beta between a tangent line passing through a contact point of the slide sheet 7 and the swing rod 10 and the upper side surface of the slide sheet 7 is 5 degrees, the speed of the valve sheet contact part 1003 protruding out of the limit surface 902 is 2.2 m/s.

Therefore, the inventor finds that the speed of the valve sheet contact part 1003 protruding the limiting surface 902 can be reduced by reducing the included angle β between the tangent of the contact point of the slide sheet 7 and the swing rod 10 and the upper end surface of the slide sheet 7 when the valve sheet contact part 1003 protrudes the limiting surface 902. Wherein beta is less than or equal to 10 degrees, which meets the design requirement.

Further, the inventors conducted a reliability experiment for the valve sheet contact portion 1003 and the air release valve sheet 8 at different β values, and found table 1 below.

TABLE 1 reliability results of valve plate contact and bleed valve plate at different beta values

According to experimental data, when an included angle beta between a tangent line of a contact point of the sliding sheet 7 and the swing rod 10 and the upper side face of the sliding sheet 7 is 10 degrees or less, the reliability of the valve sheet contact part 1003 and the exhaust valve sheet 8 is not problematic; theoretically, the smaller beta is, the better the reliability is, but if the beta is too small, the swing amplitude of the swing rod 10 is too small, the exhaust valve plate 8 cannot be completely closed, so the size of the beta needs to be combined with the actual design, and the beta is not suitable to be larger than 10 degrees, namely the beta is not larger than 10 degrees.

In some embodiments, β ≦ 5 ° for the maximum rotational speed of the piston 3 of 150 rpm or greater. For the higher the highest rotation speed of the piston 3 is, the faster the speed of the valve plate contact part 1003 protruding out of the limit surface 902 is, the larger the impact force of the exhaust valve plate 8 on the swing rod 10 is, and at this time, the smaller the included angle β between the tangent of the contact point of the slide plate 7 and the swing rod 10 and the upper side surface of the slide plate 7 needs to be designed, so that β is preferably not more than 5 °.

In some embodiments, the crank angle is α, where α ≧ 280 °, when the surface of the plate contact portion 1003 facing the vent 2 is flush or tangential to the stopper surface 902 to contact the vent plate 8. Because the exhaust valve plate 8 is pressed and closed by the swing rod 10 for a long time after the exhaust hole 2 is opened, the exhaust flow area of the exhaust hole 2 is large and long, and the exhaust resistance loss is reduced, thereby ensuring higher energy efficiency; and alpha is more than or equal to 280 degrees, the moment of the fastest speed of the sliding sheet 7 when the crank angle is 270 degrees is avoided, and therefore the swinging speed of the swinging rod 10 is further reduced.

In some embodiments, as shown in fig. 9 to 11, the slider 7 has a swing link contact part 701 for contacting the swing link 10, and the swing link contact part 701 is a corner part between an upper side surface of the slider 7 and an outer end surface of the slider 7. Specifically, the rocker contact 701 contacts the slider contact 1002, and the surface of the rocker contact 701 is an arc surface. In other words, the surfaces of the rocker contact portion 701 and the slider contact portion 1002 are circular arc surfaces, which are easier to process and measure than other curved circular arc surfaces, and which also better control the movement of the rocker 10.

In some embodiments, a surface of at least one of the blade contact 1003 and the vane contact 1002 is coated with a wear resistant coating. Preferably, the surfaces of the valve sheet contact 1003 and the vane contact 1002 are coated with a wear resistant coating. Specifically, the wear-resistant coating may be a teflon coating or a DLC coating to improve the wear resistance of the surface of the slider contact portion 1002, thereby improving the reliability of the operation of the swing link 10.

In other embodiments, a wear member is embedded in a surface of at least one of blade contact 1003 and slide contact 1002. Preferably, wear-resistant pieces are embedded in the surfaces of the valve sheet contact part 1003 and the slide sheet contact part 1002. Specifically, the wear-resistant member is made of an elastic material, which is rubber or spring steel, and further, the spring steel may be 65mn, 55si2mn, 60si2mnA, 50CrVA, SUS301, SUS304, or the like. So as to improve the wear resistance of the surface of the contact portion 1002 of the sliding piece and further improve the reliability of the operation of the swing link 10.

In the embodiment of the present invention, the swing link 10 drives the exhaust valve plate 8 to close the exhaust hole 2 when the sliding vane 7 moves outward, which should be broadly understood as follows.

In some embodiments, after the sliding piece 7 moves outward from the inner limit position by a predetermined distance, the valve sheet contact portion 1003 of the swing link 10 contacts the vent valve sheet 8 to drive the vent valve sheet 8 to close the vent hole 2. In other words, before the sliding vane 7 moves from the inner limit position to the outer limit position by the predetermined distance, the valve sheet contact portion 1003 of the swing link 10 moves toward the exhaust valve sheet 8, but does not contact the exhaust valve sheet 8, the exhaust valve sheet 8 is not driven, and the valve sheet contact portion 1003 contacts the exhaust valve sheet 8 after the sliding vane 7 moves by the predetermined distance, and the exhaust valve sheet 8 is driven to move toward the exhaust hole 2 to close the exhaust hole 2.

In some embodiments, the upper bearing 5 is located at an upper end provided above the cylinder 1 to close the cylinder chamber 101, the lower bearing 6 is located at a lower end provided below the cylinder 1 to close 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.

As shown in fig. 2 and 3, in some embodiments of the present invention, the discharge valve sheet 8 is a reed valve sheet, and the discharge air has a fixed end 801 fixed to the upper bearing 5 and a free end 802 for opening and closing the discharge air hole 2. The fixed end 801 of the discharge valve plate 8 is provided with a fixing hole 803, and the fixed end 801 of the discharge valve plate 8 is fixed to the upper bearing 5 by, for example, a bolt, welding, riveting, or other fixing means. Because the exhaust valve plate 8 closes the exhaust hole 2 through the elasticity of the exhaust valve plate and the driving of the swing rod 10, the exhaust valve plate 8 has no rigidity. It should be understood that the present invention is not limited thereto, for example, the exhaust valve plate 8 may not be fixed, and may be opened by the gas thrust, and may be completely closed by the driving of the swing link 10, in which case, the exhaust valve plate 8 may also be referred to as a non-rigid exhaust valve plate 8.

In some embodiments, as shown in fig. 2 and 3, a receiving groove 501 is formed on the upper surface of the upper bearing 5, and the air release valve sheet 8 is installed in the receiving groove 501. The fixed end 801 of the reed valve plate is fixed at the bottom of the receiving groove 501, the free end 802 of the exhaust hole 2 covers the exhaust hole 2, and when exhausting, the free end 802 of the reed valve plate bends under the action of gas thrust to open the exhaust hole 2.

In some embodiments, as shown in fig. 8, when the exhaust valve plate 8 closes the exhaust hole 2, a projection area of the exhaust hole 2 on the exhaust valve plate 8 is set as a windward area 804 of the exhaust valve plate 8, and a contact position of the swing link 10 when contacting the exhaust valve plate 8 is located in the windward area 804. Preferably, the diameter of the windward region 804 is equal to the diameter of the exhaust vent 2. The contact position of the swing rod 10 and the exhaust valve plate 8 is located in the windward area 804, when the swing rod 10 presses the exhaust valve plate 8 to close the exhaust hole 2, the exhaust hole 2 is closed stably, the exhaust valve plate 8 is not prone to rebound or warping when the exhaust hole 2 is closed, and the closeness of the exhaust hole 2 is improved.

The number of the exhaust holes 2 can be one or more, the swing rod 10 is arranged corresponding to at least one exhaust hole 2, namely, an exhaust valve plate 8 for opening and closing at least one exhaust hole 2 is driven by the swing rod 10. Preferably, the swing links 10 are disposed in one-to-one correspondence with the exhaust holes 2.

As shown in fig. 2, 4-5 and 7, in some embodiments, the compression mechanism 300 further includes a lift limiter 9, the lift limiter 9 is configured to limit a lift of the exhaust valve plate 8, that is, limit a lift of a free end 802 of the exhaust valve plate 8, the lift limiter 9 is provided with an avoiding hole 901 for avoiding the swing link 10, and the swing link 10 may pass through the avoiding hole 901 to contact the free end 802 of the exhaust valve plate 8 to drive the exhaust valve plate 8. It is understood that the relief hole 901 may be a circumferentially open hole, as shown in fig. 7, or a closed hole, as shown in fig. 13. The specific form of the avoiding hole 901 may be designed according to the specific form of the swing link 10, so as to avoid interference with the swing link 10.

In some embodiments, 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.

In some embodiments, as shown in fig. 6 and 9 to 11, 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 lever 1001, the vane contact 1002 and the valve sheet contact 1003 are integrated with the lever 1001, and the valve sheet contact 1003 may be fixed to the lever 1001 by welding, screwing, or the like. In the embodiment shown in FIGS. 9-11, slider contact 1002 is formed by the second end or a portion of the second end of rod 1001.

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 may 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 as to prevent the sliding piece 7 from colliding with the sliding piece contact portion 1002 during movement, reduce noise generated during operation of the compression mechanism 300, and improve the service life of the swing rod 10 and the swing rod 10.

In some embodiments, as shown in fig. 7A and 7B, the compression mechanism 300 further includes a lift stopper 9, and the lift stopper 9 is disposed above the exhaust valve sheet 8. The lift limiter 9 is used for limiting the lift of the exhaust valve plate 8, namely limiting the lift of the free end 802 of the exhaust valve plate 8, the lift limiter 9 is provided with an avoiding hole 901 for avoiding the swing rod 10, and the swing rod 10 can penetrate through the avoiding hole 901 to be in contact with the free end 802 of the exhaust valve plate 8 so as to drive the exhaust valve plate 8. When the valve plate contact part 1003 moves downwards, the valve plate contact part 1003 passes through the avoiding hole 901 to be in contact with the exhaust valve plate 8, so that the swing rod 10 does not interfere with the lift limiter 9.

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 swing link 10 in the axial direction of the pivot 11, the swing link 10 is supported by the pivot 11 to swing in a groove formed in the upper bearing 5, the groove width is b, the swing link 10 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 hole 1004 of the pivot 11 on the upper bearing 5, the diameter d1 of the hole 1004 of the pivot 11 of the rocker 10, 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.

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 13, 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 901 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 13, 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. 13 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. 12, 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.

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 above 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 is internally provided with a cylinder chamber and a slide sheet groove;

an exhaust port in communication with the cylinder chamber;

a piston;

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

an upper bearing and a lower bearing that rotatably support the crankshaft;

the sliding sheet is arranged in the sliding sheet groove and can move back and forth between an inner limit position and an outer limit position, and the inner end of the sliding sheet is abutted against the piston;

the exhaust valve plate is used for opening and closing the exhaust hole;

the lift limiter is provided with a limiting surface used for limiting the lift of the exhaust valve plate;

the swing rod is driven to swing around a pivot when the sliding sheet moves outwards so as to enable the swing rod to push the exhaust valve sheet to close the exhaust hole, the swing rod is provided with a valve sheet contact part used for being in contact with the exhaust valve sheet and a sliding sheet contact part used for being in contact with the sliding sheet,

the sliding sheet is provided with a swinging rod contact part used for being in contact with the swinging rod, the surface of the swinging rod contact part is a curved surface, when the surface of the valve sheet contact part facing the exhaust hole is flush or tangent with the limiting surface, an included angle beta is formed between a tangent line passing through the contact point of the sliding sheet and the swinging rod and the upper side surface of the sliding sheet on the central longitudinal section of the sliding sheet groove, and the beta is less than or equal to 10 degrees.

2. The compression mechanism as set forth in claim 1, wherein β ≦ 5 ° for the maximum rotation speed of the piston of 150 rpm or more.

3. The compressing mechanism as claimed in claim 1, wherein the crank angle is α when the surface of the plate contacting portion facing the exhaust hole is flush with or tangent to the stopper surface to contact the exhaust plate, where α ≧ 280 °.

4. The compression mechanism as claimed in claim 1, wherein the surface of said rocker contact portion is a circular arc surface.

5. The compression mechanism of claim 4, wherein the rocker contact is a corner between an upper side surface of the vane and an outer end surface of the vane.

6. The compression mechanism of claim 1, wherein a surface of at least one of the valve plate contact portion and the vane contact portion is coated with a wear resistant coating.

7. The compression mechanism of claim 1, wherein a wear member is embedded in a surface of at least one of the valve plate contact portion and the vane contact portion.

8. The compressing mechanism as claimed in claim 1, wherein the swing link contacts the discharge valve plate after the sliding piece moves outward from the inner limit position by a predetermined distance to drive the discharge valve plate to close the discharge hole.

9. The compressing mechanism as set forth in claim 1, wherein the discharge hole is formed on the upper bearing, and the discharge valve sheet is a reed valve sheet and has a fixed end fixed on the upper bearing and a free end for opening and closing the discharge hole.

10. A rotary compressor characterized by comprising the compression mechanism according to any one of claims 1 to 9.

11. A refrigerating apparatus comprising the rotary compressor of claim 10.