CN111720317B

CN111720317B - Compression mechanism and rotary compressor with same

Info

Publication number: CN111720317B
Application number: CN202010605281.9A
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: CN111720317A

Abstract

The invention discloses a compression mechanism and a rotary compressor with the same. The compression mechanism comprises a cylinder, an exhaust hole, a piston, a crankshaft, an upper bearing, a lower bearing, a sliding sheet, a lift limiter, an exhaust valve plate and a swing rod; when the sliding vane moves outwards, the swing rod is driven to swing so as to enable the swing rod to push the exhaust valve plate to close the exhaust hole, and the swing rod is provided with a valve plate contact part and a sliding vane contact part; the distance between the contact part of the valve plate and the exhaust hole is h1, the thickness of the exhaust valve plate is t, and when the slide sheet is positioned at the outer limit position, h1-t is less than or equal to 0.3 mm; when the slide sheet moves towards the outer limit position and just contacts the exhaust valve sheet, the rotation angle of the crankshaft is beta, wherein the beta is more than or equal to 270 degrees; when the crank angle is in the range of 180-beta, the rotation angle of the oscillating bar is alpha 1, when the crank angle is in the range of beta-360 degrees, the rotation angle of the oscillating bar is alpha 2, and alpha 1 is less than alpha 2. The exhaust valve plate of the compression mechanism has good timeliness and reliability in closing, low noise and high energy efficiency.

Description

Compression mechanism and rotary compressor with same

Technical Field

The invention relates to the technical field of compressors, in particular to a compression mechanism and a rotary 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 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 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 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, and 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 distance between the valve plate contact part and the outlet face of the exhaust hole is h1, the thickness of the exhaust valve plate is t, when the slide plate is located at the outer limit position, h1-t is less than or equal to 0.3 mm, when the slide plate moves towards the outer limit position and the surface, facing the exhaust hole, of the valve plate contact part is flush with or tangent to the limiting face, the crank angle is beta, wherein beta is greater than or equal to 270 degrees, when the position of the oscillating bar is taken as a reference when the crank angle is beta, the rotation angle of the oscillating bar is alpha 1 when the crank angle is within the range of 180 degrees to beta, the rotation angle of the oscillating bar is alpha 2 when the crank angle is within the range of beta-360 degrees, and alpha 1 is less than alpha 2.

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 exhaust valve sheet can be a rigid valve sheet, the opening is easy, 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 slide sheet is located at the outer limit position, h1-t is less than or equal to 0.3 mm, so that the swing rod is ensured to push the exhaust valve sheet to close the exhaust hole in time, gas backflow is avoided, and the energy efficiency of the compression mechanism is improved. Moreover, as alpha 1 is less than alpha 2, namely before the valve plate contact part of the swing rod contacts the exhaust valve plate, the swing amplitude of the swing rod is small, in other words, the speed of the valve plate contact part contacting the exhaust valve plate is small, and the contact reliability of the valve plate contact part and the exhaust valve plate is ensured; on the other hand, as alpha 1 is less than alpha 2, after the valve sheet contact part of the swing rod contacts the exhaust valve sheet, the valve sheet contact part quickly presses the exhaust valve sheet and closes the exhaust hole, so that gas backflow is reduced, and the energy efficiency of the compression mechanism is improved.

In some embodiments, the sliding piece has a swing rod contact portion for contacting with the swing rod, a surface of the swing rod contact portion is an arc surface, the surface of the sliding piece contact portion includes a plane section and an arc surface section tangent to the plane section, and when the sliding piece moves outwards, the sliding piece contacts with the plane section first.

In some embodiments, the slider has a rocker contact portion for contacting the rocker, a surface of the rocker contact portion is a circular arc surface, and the surface of the slider contact portion includes a first planar section, a second planar section, and a circular arc surface section connected between the first planar section and the second planar section.

In some embodiments, the included angle between the first planar segment and the second planar segment is θ 1, wherein 25 ° ≦ θ 1 ≦ 45 °.

In some embodiments, the radius of the arc of the surface of the rocker contact is less than or equal to the radius of the arc segment.

In some embodiments, when the surface of the valve plate contact portion facing the exhaust hole is flush with or tangent to the limiting surface to contact the exhaust valve plate, on a central longitudinal section of the slide plate groove, an included angle θ is formed between a tangent line passing through a contact point of the slide plate and the swing rod and an upper side surface of the slide plate, wherein θ is less than or equal to 10 °.

In some embodiments, the arc surface segment has an arc radius R, wherein R is greater than or equal to 3 mm and less than or equal to 6 mm.

In some embodiments, the arc radius of the surface of the rocker contact is R1, wherein R1 is 1 mm 3 mm.

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 schematic view of a sliding vane of a compression mechanism according to an embodiment of the present invention.

Fig. 10 is a view illustrating a state in which a rocker lever of a compression mechanism is about to close an exhaust valve sheet according to an embodiment of the present invention.

FIG. 11 is a diagram illustrating the movement of the rocker arm at a crank angle of 180- β in the compression mechanism according to the embodiment of the present invention.

FIG. 12 is a diagram illustrating the movement of the rocker arm at a crank angle of β -360 ° in the compression mechanism according to the embodiment of the present invention.

Fig. 13 is a schematic diagram of the compression mechanism according to the embodiment of the present invention with a crank angle of 0 ° or 360 °.

Fig. 14 is a schematic view of a compression mechanism according to an embodiment of the present invention having a crank angle of 180 °.

Reference numerals:

100. a housing;

200. a motor;

300. a compression mechanism;

1. a cylinder; 101. a cylinder chamber; 102. a slide groove; 1021. avoiding the notch;

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; 10021. a first planar segment; 10022. a circular arc surface section; 10023. a second planar segment; 10024. a hook 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, a lift stopper 9, an exhaust valve plate 8, 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. 14. 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 °, which is a rotation angle of the compressor, as shown in fig. 13.

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 when the exhaust valve sheet 8 is exhausted. The swing rod 10 has a valve sheet contact portion 1003 and a slide sheet contact portion 1002, the valve sheet contact portion 1003 is used for contacting with the exhaust valve sheet 8, and the slide sheet contact portion 1002 is used for contacting with the slide sheet 7. The swing rod 10 drives the exhaust valve plate 8 to close the exhaust hole 2 when the sliding sheet 7 moves outwards, and it can be understood that the swing rod 10 is linked with the sliding sheet 7, and when the sliding sheet 7 moves outwards from the inner limit position to the outer limit position, the sliding sheet 7 drives the sliding sheet contact part 1002 of the swing rod 10 to move, so that the swing rod 10 swings around the pivot 11 to enable the valve plate contact part 1003 of the swing rod 10 to push the exhaust valve plate 8 to close the exhaust hole 2. 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.

As shown in fig. 10 to 12, the distance from the valve sheet contact part 1003 to the outlet surface of the exhaust hole 2 is h1, the thickness of the exhaust valve sheet 8 is t, and when the slide sheet 7 is located at the outer limit position, that is, when the exhaust is finished, h1-t is less than or equal to 0.3 mm. When the slide plate 7 moves towards the outer limit position and the surface of the valve plate contact part 1003 facing the exhaust hole 2 is flush with or tangent to the limit surface 902, namely the valve plate contact part 1003 protrudes out of the limit surface 902 and just contacts with the exhaust valve plate 8, the crank angle is beta, wherein beta is larger than or equal to 270 degrees. Taking the position of the oscillating bar 10 when the crank angle is beta as a reference, when the crank angle is within the range of 180 degrees to beta, the rotation angle of the oscillating bar 10 is alpha 1, as shown in fig. 11, the angle of the oscillating bar 10 swinging around the axis of the pivot 11, i.e. the rotation angle of the oscillating bar 10 is alpha 1. When the crank angle is in the range of beta-360 degrees, the rotation angle of the swing rod 10 is alpha 2, as shown in fig. 12, the swing rod 10 swings around the axis of the pivot 11, that is, the rotation angle of the swing rod 10 is alpha 2, wherein alpha 1 is less than alpha 2.

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 assistance of the swing rod 10, the rigidity design of the exhaust valve plate 8 is flexible, and the exhaust valve plate 8 can be designed to have no rigidity (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, and the exhaust noise is reduced.

When the exhaust of the exhaust hole 2 is finished, h1-t is less than or equal to 0.3 mm; so as to ensure that the swing rod 10 pushes the exhaust valve plate 8 to close the exhaust hole 2 in time, thereby avoiding gas backflow and being beneficial to improving the energy efficiency of the compression mechanism 300. When the surface of the valve plate contact part 1003 facing the exhaust hole 2 is flush or tangent with the limiting surface 902, the crank angle beta is not less than 270 degrees, so that the exhaust valve plate 8 is in a larger opening degree in the early stage of exhaust and is maintained for a longer time, and the exhaust flow area of the exhaust hole 2 is increased to improve the energy efficiency of the compression mechanism 300. Further, as α 1 is less than α 2, that is, before the valve sheet contact portion 1003 of the swing rod 10 contacts the exhaust valve sheet 8, the swing amplitude of the swing rod 10 is smaller, in other words, the speed of the valve sheet contact portion 1003 contacting the exhaust valve sheet 8 is smaller, so as to ensure the reliability of the valve sheet contact portion 1003 contacting the exhaust valve sheet 8; on the other hand, since α 1 is less than α 2, after the valve sheet contact portion 1003 of the swing rod 10 contacts the exhaust valve sheet 8, the valve sheet contact portion 1003 rapidly presses the exhaust valve sheet 8 and closes the exhaust hole 2, so that gas backflow is avoided, and the energy efficiency of the compression mechanism 300 is improved.

When the crank angle is 180 degrees to beta, the inventor conducts 500-hour reliability experiments aiming at that the rotation angles alpha 1 of different swing rods 10 are respectively 5 degrees, 8 degrees, 12 degrees and 15 degrees as follows.

Specifically, when the surface of the valve sheet contact portion 1003 facing the exhaust hole 2 is flush with or tangent to the limit surface 902, the crank angle β is 270 °, h1-t is 0, the rotation angle α 2 of the swing link 10 corresponding to the crank angle β -360 ° is 10 °, the rotation speed of the compression mechanism 300 is 120 rpm/sec, the refrigerant is R32, the displacement of the cylinder 1 is 10 cubic centimeters, the diameter of the exhaust hole 2 is 6.5 millimeters, the inner diameter of the cylinder 1 is 43 millimeters, the length of the slide vane 7 is 21 millimeters, the eccentric amount of the crankshaft 4 is 4.25 millimeters, the lift of the exhaust valve sheet 8 is 2 millimeters, the distance X from the center of the pivot 11 to the center of the bearing 5 is 34.5 millimeters, the distance from the center of the pivot 11 to the end surface Y of the bearing 5 is 2.9 millimeters, the distance L from the valve sheet contact portion 1003 to the center of the pivot 11 is 15 millimeters, the arc radius R1 of the swing link contact portion 701 is 2 millimeters, and the radius R of the slide sheet contact portion 1002 is 5 millimeters, as shown in fig. 6 and 9.

The test results are as follows: when the rotation angle α 1 of the swing rod 10 is 5 ° and 8 °, the reliability of the valve sheet contact part 1003 and the exhaust valve sheet 8 passes; when the rotation angle alpha 1 of the oscillating bar 10 is 12 degrees, the valve sheet contact part 1003 is obviously abraded, and the reliability is invalid; when the rotation angle alpha 1 of the swing rod 10 is 15 degrees, the valve sheet contact part 1003 and the exhaust valve sheet 8 are both obviously abraded, and the reliability is invalid.

In summary, the larger the rotation angle α 1 of the valve sheet contact portion 1003 before contacting the exhaust valve sheet 8, the more serious the abrasion of the swing link 10 and the exhaust valve sheet 8, and the larger the rotation angle α 1 of the swing link 10, the larger the installation space is required, so as to ensure the reliability and the assembly performance of the compression mechanism 300. Therefore, when the slide sheet 7 moves towards the outer limit position, the compression rotation angle 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 is beta, and beta is larger than or equal to 270 degrees; when the crank angle is within the range of 180-beta, the rotation angle of the oscillating rod 10 is alpha 1, and when the crank angle is within the range of beta-360 degrees, the rotation angle of the oscillating rod 10 is alpha 2, which meets the condition that alpha 1 is less than alpha 2; and when the exhaust is finished, namely the slide sheet 7 is positioned at the outer limit position, h1-t is less than or equal to 0.3 mm.

In some embodiments, as shown in fig. 6 and 10-12, the slider 7 has a rocker contact 701 for contacting the rocker 10. Specifically, the swing link contact part 701 is disposed at the outer end of the slide 7 and on a side close to the swing link 10, and a contact position between the swing link contact part 701 and the swing link 10 is an arc surface. The surface of the slider contact portion 1002 on the side close to the slider 7 includes a plane section and a circular arc section 10022, and the plane section is tangent to the circular arc section 10022, in other words, the plane section smoothly transitions to the circular arc section 10022. When the sliding piece 7 moves outwards, the sliding piece 7 is firstly contacted with the plane section. That is, the circular arc surface segment 10022 is closer to the outer end of the slide slot 102 than the flat surface segment. Further, one side of the sliding piece contact part 1002 departing from the arc surface segment 10022 is provided with a round chamfer, the sliding piece contact part 1002 is provided with a hook 10024 extending in the direction of the sliding piece 7, one side of the outer end of the sliding piece groove 102 close to the swing rod 10 is provided with an avoiding notch 1021, and when the sliding piece 7 moves to an outer limit position, the swing rod contact part 701 and the hook 10024 both move to the avoiding notch 1021.

When the sliding sheet 7 moves outwards to push the swing rod 10 to swing, the swing rod contact part 701 is firstly contacted with the plane section, so that when the valve sheet contact part 1003 is contacted with the exhaust valve sheet 8, the speed of the swing rod 10 impacting the exhaust valve sheet 8 is low, and the reliability of the valve sheet contact part 1003 and the exhaust valve sheet 8 in working is improved. When the swing link contact part 701 slides across the plane section and contacts with the arc surface section 10022, the swing link 10 is accelerated to swing due to the guiding action of the arc surface section 10022, so that the valve sheet contact part 1003 accelerates to press the exhaust valve sheet 8 downwards, and the exhaust valve sheet 8 can be pushed to close the exhaust hole 2 in a short time. That is, when the sliding piece 7 moves outward to push the swing rod 10 to swing, the swing rod 10 swings at a slow speed and then at a fast speed, and at this time, the displacement of the exhaust hole 2 is large first and then small, when the displacement is large, the swing rod 10 needs to be pressed at a slow speed, and when the displacement is small, the swing rod 10 presses the exhaust valve plate 8 at a fast speed, thereby improving the energy efficiency of the compression mechanism 300.

In other embodiments, as shown in fig. 6 and 9-12, the slide 7 has a rocker contact 701 for contacting the rocker 10. Specifically, the swing link contact part 701 is disposed at the outer end of the slide 7 and on a side close to the swing link 10, and a contact position between the swing link contact part 701 and the swing link 10 is an arc surface. Further, the surface of the slide contact 1002 includes a first planar segment 10021, a second planar segment 10023, and a circular arc segment 10022 connected between the first planar segment 10021 and the second planar segment 10023, specifically, the first planar segment 10021, the second planar segment 10023, and the circular arc segment 10022 are smoothly transitioned. When the sliding piece 7 moves outwards to push the swing rod 10 to swing, the sliding piece 7 is sequentially contacted with the first plane section 10021, the second plane section 10023 and the arc surface section 10022 of the sliding piece contact part 1002, and because the included angle between the first plane section 10021 and the upper end face of the sliding piece 7 is smaller, the included angle between the second plane section 10023 and the upper end face of the sliding piece 7 is increased by the arc surface section 10022 in the swing rod 10; when the valve plate contact part 1003 is in contact with the exhaust valve plate 8, the speed of the swing rod 10 impacting the exhaust valve plate 8 is low; and the exhaust valve sheet 8 is pressed down at an accelerated speed after the valve sheet contact part 1003 protrudes out of the limiting surface 902, so that the valve sheet contact part 1003 can push the exhaust valve sheet 8 to close the exhaust hole 2 in a short time.

Further, as shown in fig. 6, the included angle between the first planar segment 10021 and the second planar segment 10023 is θ 1, wherein θ 1 is greater than or equal to 25 ° and less than or equal to 45 °. After valve block contact portion 1003 towards exhaust hole 2's surface and spacing face 902 parallel and level or tangent and contact exhaust valve block 8, need valve block contact portion 1003 to press exhaust valve block 8 fast and close exhaust hole 2 to reduce gaseous backward flow, guarantee that compressing mechanism 300 has the high energy efficiency, because the speed of pressing depends on the contained angle of being promoted plane and gleitbretter 7, but if the contained angle is too big, the phenomenon of auto-lock can appear in pendulum rod 10 and gleitbretter 7, reduces the reliability of pendulum rod 10 work. Therefore, θ 1 satisfies: theta 1 is more than or equal to 25 degrees and less than or equal to 45 degrees.

In some embodiments, the radius of the arc of the surface of the rocker contact 701 is less than or equal to the radius of the arc segment 10022. The sliding sheet 7 can be more coherent when the oscillating bar 10 is pushed to move, noise generated when the sliding sheet 7 is linked with the oscillating bar 10 is avoided, and the working reliability of the compression mechanism 300 is improved.

Further, the inventors found through research that the size of the arc radius of the arc surface segment 10022 mainly depends on the crank angle of the valve plate contact portion 1003 when protruding out of the limit surface 902; the larger the crank angle is, the shorter the time the swing link 10 is to press the exhaust valve plate 8 to close the exhaust hole 2, and accordingly, the smaller the arc radius of the arc surface segment 10022 is, the faster the swing link 10 swings. As shown in fig. 6 and 9, optionally, the arc radius of the arc surface segment 10022 is R, wherein R is greater than or equal to 3 mm and less than or equal to 6 mm; the arc radius of the surface of the swing link contact part 701 is R1, wherein R1 is more than or equal to 1 mm and less than or equal to 3 mm.

In some embodiments, when the surface of the valve sheet contact portion 1003 facing the exhaust hole 2 is flush with or tangent to the limiting surface 902 to contact the exhaust valve sheet 8, on the central longitudinal section of the slide sheet groove 102, an included angle θ is formed 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, where θ is less than or equal to 10 °, so as to reduce the impact speed of the valve sheet contact portion 1003 and the exhaust valve sheet 8 and improve the reliability of the operation of the compression mechanism 300.

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 can be a non-rigid exhaust valve plate. 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 and 4-6 and 10-12, in some embodiments, the swing link 10 includes a rod 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.

In some embodiments, as shown in fig. 6 and 10 to 12, 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. 10 and 12, slider contact 1002 is formed by the second end or a portion of the second end of lever 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 lift limiter 9 is disposed above the exhaust valve sheet 8. The lift limiter 9 is provided with an avoiding hole 901 for avoiding the swing rod 10, and the swing rod 10 can pass 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 sheet contact portion 1003 moves downward, the valve sheet contact portion 1003 passes through the avoiding hole 901 to contact the exhaust valve sheet 8, so that the swing link 10 does not interfere with the lift stopper 9, and in this embodiment, the avoiding hole 901 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 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 14, 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 therein, 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.

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,

wherein the distance between the valve plate contact part and the outlet surface of the exhaust hole is h1, the thickness of the exhaust valve plate is t, when the slide plate is positioned at the outer limit position, h1-t is less than or equal to 0.3 mm,

wherein when the slide plate moves towards the outer limit position and the surface of the valve plate contact part facing the exhaust hole is flush with or tangent to the limit surface, the crank angle is beta, wherein beta is more than or equal to 270 degrees,

the position of the oscillating bar when the crank angle is beta is taken as a reference, when the crank angle is within the range of 180-beta, the rotation angle of the oscillating bar is alpha 1, when the crank angle is within the range of beta-360 degrees, the rotation angle of the oscillating bar is alpha 2, and alpha 1 is less than alpha 2.

2. The compressing mechanism as set forth in claim 1, wherein the slide piece has a swing link contact portion for contacting the swing link, a surface of the swing link contact portion is a circular arc surface, the surface of the slide piece contact portion includes a plane section and a circular arc surface section tangent to the plane section, and the slide piece is first in contact with the plane section when the slide piece moves outward.

3. The compression mechanism as claimed in claim 1, wherein the slider has a rocker contact portion for contacting the rocker, the rocker contact portion having a surface that is a circular arc, the surface of the slider contact portion including a first planar section, a second planar section, and a circular arc section connected between the first planar section and the second planar section.

4. The compression mechanism of claim 3, wherein the included angle between the first planar segment and the second planar segment is θ 1, wherein θ 1 is 25 ° or more and 45 ° or less.

5. The compression mechanism as claimed in claim 2 or 3, wherein the radius of the arc of the surface of the rocker contact portion is smaller than or equal to the radius of the arc surface segment.

6. The compressing mechanism as claimed in any one of claims 1 to 3, wherein when the surface of the valve plate contact portion facing the exhaust hole is flush or tangential to the limiting surface to contact the exhaust valve plate, an included angle θ is formed between a tangent line passing through a contact point of the slide plate and the swing rod and an upper side surface of the slide plate on a central longitudinal section of the slide plate groove, where θ is not more than 10 °.

7. The compression mechanism as claimed in claim 2 or 3, wherein the arc radius of the arc surface segment is R, wherein R is 3 mm ≦ R ≦ 6 mm.

8. The compression mechanism as claimed in claim 2 or 3, wherein the radius of the arc of the surface of the rocker contact is R1, where R1 ≦ 3 mm 1 mm.

9. A rotary compressor characterized by comprising the compression mechanism according to any one of claims 1 to 8.

10. A refrigerating apparatus comprising the rotary compressor of claim 9.