CN111720321B

CN111720321B - Compression mechanism

Info

Publication number: CN111720321B
Application number: CN202010606529.3A
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: 2022-04-15
Anticipated expiration: 2040-06-29
Also published as: CN111720321A

Abstract

The invention discloses a compression mechanism. The compression mechanism includes: 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; 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 swing rod drives the swing rod to swing around a pivot when the sliding sheet moves outwards so that the swing rod pushes the exhaust valve sheet to close the exhaust hole; and the elastic piece is used for applying elastic force to the swing rod so as to enable the swing rod to be always kept in contact with the sliding piece. The exhaust valve plate of the compression mechanism has the advantages of good applicability and reliability, low closing noise and high energy efficiency.

Description

Compression mechanism

Technical Field

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

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 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 that the exhaust valve plate is fully opened, so that the exhaust valve plate is easy to vibrate, the exhaust resistance loss is large, the problem of noise caused by airflow pulsation is easy to cause, and the problem of noise generated by collision between parts when the compression mechanism works is solved.

Disclosure of Invention

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

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

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

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 rotary 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 swing rod drives the swing rod to swing around a pivot when the sliding sheet moves outwards so that the swing rod pushes the exhaust valve sheet to close the exhaust hole; and the elastic piece is used for applying elastic force to the swing rod so as to enable the swing rod to be always kept in contact with the sliding piece.

According to the compression mechanism provided by the embodiment of the invention, when the slide sheet moves from the inner limit position to the outer limit position, namely the slide sheet moves along the center far away from the cylinder chamber, the 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, and the exhaust valve sheet closes the exhaust hole by virtue of the driving force of the swing rod, so that the timeliness and the reliability of closing the exhaust valve sheet can be improved, the exhaust valve sheet has no rigidity and is easy to open, the loss of exhaust resistance is reduced, the design flexibility and the applicability of the exhaust valve sheet are improved, the exhaust noise is reduced, and the slide sheet is always kept in contact with the slide sheet under the action of the elastic element, so that the slide sheet cannot collide with the swing rod, and the noise is reduced.

In some embodiments, the swing rod contacts the air release valve plate when the slide plate is at the inner limit position or contacts the air release valve plate after the slide plate moves outwards from the inner limit position for a predetermined distance, so as to drive the air release valve plate to close the air release hole.

In some embodiments, the resilient member is a coil spring, a leaf spring, or a torsion spring.

In some embodiments, the elastic member is a conical helical compression spring, the thin end of the conical helical compression spring is connected with the swing rod, the linear diameter of the conical helical compression spring is phi 1, the free length of the conical helical compression spring is L3, the intermediate diameter of the conical helical compression spring is phi 2, wherein L3 is more than or equal to 4 mm and less than or equal to 10 mm, phi 1 is more than or equal to 0.3 mm and less than or equal to 0.5 mm, and phi 2 is more than or equal to 3 mm and less than or equal to 6 mm.

In some embodiments, the distance between the force application position of the elastic element acting on the swing rod and the central axis of the pivot is L, wherein L is more than or equal to 3 mm and less than or equal to 7 mm.

In some embodiments, when the crank angle of the crankshaft is in the range of 0 to 180 degrees, the distance between the force application position of the elastic member acting on the swing link and the central axis of the pivot is L, the elastic force of the elastic member is F, the moment of inertia of the swing link relative to the pivot is J, and the rotation angular speed of the swing link is α, wherein F ≧ ja/L.

In some embodiments, the spring member has a spring constant K, wherein K is 0.3N/mm or less and 1.0N/mm or less.

In some embodiments, the pivot is mounted on the upper bearing, a first end of the elastic member is connected to the upper bearing, and a second end of the elastic member is connected to the swing link.

In some embodiments, the vent hole is multiple, and the swing rod is arranged corresponding to at least one vent hole.

In some embodiments, the lifting device further comprises a lifting limiter, wherein the lifting limiter is used for limiting the lifting range of the exhaust valve plate and is provided with an avoidance hole used for avoiding the swing rod.

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

A compression mechanism according to another embodiment of the present invention includes: the air cylinder is internally provided with a cylinder chamber and a slide sheet groove; 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; an exhaust hole formed on the upper bearing, the exhaust hole communicating with the cylinder chamber; the exhaust valve plate is used for opening and closing the exhaust hole; the swing rod can swing around the pivot, and is linked with the sliding sheet, so that the swing rod is driven to swing to push the exhaust valve sheet to close the exhaust hole when the sliding sheet moves outwards; and the elastic piece is arranged between the upper bearing and the oscillating bar and is used for pushing the oscillating bar to be always in contact with the sliding piece.

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. 5A is a perspective view of an elastic member of a compression mechanism according to an embodiment of the present invention.

Fig. 5B is a sectional view of an elastic member of a compression mechanism according to an embodiment of the present invention.

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 view illustrating a state in which a rocker lever of the compression mechanism contacts an exhaust valve sheet according to the embodiment of the present invention.

FIG. 11 is a schematic diagram of the pendulum arm force of the compression mechanism 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 °.

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;

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;

12. an elastic member.

Detailed Description

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

A compression mechanism and a rotary compressor according to an embodiment of the present invention will be described with reference to fig. 1 to 13.

As shown in fig. 1, a rotary compressor according to an embodiment of the present invention includes a casing, a motor and a compression mechanism installed in the casing, the motor for driving the compression mechanism.

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 13, 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 rocker 10, and an elastic member 12.

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 of the crankshaft 4 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 of the crankshaft 4 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. When the slide sheet 7 moves outwards, the swing rod 10 is driven to swing around the pivot 11, so that the swing rod 10 pushes the exhaust valve sheet 8 to close the exhaust hole 2. In other words, the swing link 10 is linked with the sliding vane 7, and when the sliding vane 7 moves from the inner limit position to the outer limit position, for example, the sliding vane 7 directly drives the swing link 10 to swing, and then the swing link 10 drives the exhaust valve plate 8 to close the exhaust hole 2. The elastic member 12 is used for applying an elastic force to the swing link 10 so as to keep the swing link 10 in contact with the slide 7 at all times. Namely, when the sliding sheet 7 reciprocates between the inner limit position and the outer limit position, the swing rod 10 is always in contact with the sliding sheet 7 and does not separate from the sliding sheet.

As shown in fig. 1 to 4, 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 for closing the exhaust hole 2 to the exhaust valve plate 8 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, due to 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 be non-rigid (namely the exhaust valve plate 8 is not fixed), so that the exhaust valve plate 8 is easy to open, the opening degree is large, the exhaust resistance is reduced, the exhaust noise is reduced, and high energy efficiency can be ensured at both high speed and low speed. Meanwhile, the elastic element 12 applies elastic force to the swing rod 10 so that the swing rod 10 is always in contact with the sliding piece 7, so that the sliding piece 7 cannot collide with the swing rod 10 in the reciprocating movement process, and noise is reduced.

In some embodiments, as shown in fig. 4 and 6, the swing link 10 includes a rod 1001, a slide contact 1002, and a valve plate contact 1003. The pivot 11 is mounted on the upper bearing 5, and the pivot 11 is pivotally supported at the middle of the lever 1001, and the slide contact 1002 and the sheet contact 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, the valve plate contact portion 1003 contacts the discharge valve plate 8 to drive the discharge valve plate 8 to close the discharge hole 2 after the sliding plate 7 moves outward from the inner limit position by a predetermined distance. In other words, before the slide plate 7 moves from the inner limit position to the outer limit position by the predetermined distance, the valve sheet contact portion 1003 moves toward the vent valve sheet 8, but does not contact with the vent valve sheet 8, the vent valve sheet 8 is not driven, and after the slide plate 7 moves by the predetermined distance, the valve sheet contact portion 1003 contacts with the vent valve sheet 8, the vent valve sheet 8 is driven to move toward the vent hole 2 to close the vent hole 2.

In other embodiments, the valve plate contact portion 1003 contacts the discharge valve plate 8 when the slide plate 7 is at the inner limit position. In other words, when the sliding vane 7 is at the inner limit position, the valve sheet contact part 1003 is in contact with the exhaust valve sheet 8, and in the process that the sliding vane 7 moves from the inner limit position to the outer limit position, the valve sheet contact part 1003 drives the exhaust valve sheet 8 to move towards the exhaust hole 2 so as to gradually close the exhaust hole 2. Because when the gleitbretter 7 outwards moved, valve block contact site 1003 contacts with exhaust valve block 8 all the time, can slow down the instantaneous speed that exhaust valve block 8 closed exhaust hole 2, reduce the noise that the exhaust valve block 8 struck the disk seat and produced when closing exhaust hole 2.

In some embodiments, as shown in fig. 9-11, the elastic member 12 may be a torsion spring, for example, a torsion spring disposed on the pivot 11 and abutting against the swing link 10, thereby causing the slide contacting portion 1002 to always abut against the outer end of the slide 7. Alternatively, the elastic member 12 may be a plate spring, for example, a plate spring is disposed between the upper bearing 5 and the rod 1001, a first end of the plate spring is connected with the upper bearing 5, and a second end of the plate spring is connected with the rod 1001, so that the slide contact portion 1002 and the outer end of the slide 7 are always abutted. Preferably, the elastic member 12 is a conical helical compression spring, wherein a thin end of the conical helical compression spring is connected to the middle portion of the rod 1001, and a thick end of the conical helical compression spring is connected to the upper bearing 5. Optionally, a mounting groove is formed in the upper surface of the upper bearing 5, and the thick end of the conical helical compression spring is mounted in the mounting groove in an interference fit manner, so that the space is saved and the mounting is convenient.

Further, as shown in fig. 5A and 5B, the linear diameter of the conical helical compression spring is Φ 1, the free length of the conical helical compression spring is L3, the middle diameter of the conical helical compression spring is Φ 2, wherein L3 is 4 mm or more and 10 mm or less, Φ 1 is 0.3 mm or more and 0.5 mm or less, Φ 2 is 3 mm or more and 6 mm or less, specifically, the elastic coefficient of the elastic member 12 is K, wherein K is 0.3 n/mm or more and 1.0 n/mm or less.

In some embodiments, as shown in fig. 9-11, the distance between the force application position of the elastic element 12 acting on the swing link 10 and the central axis of the pivot 11 is L, wherein L is greater than or equal to 3 mm and less than or equal to 7 mm, so that a force arm with a length L is formed between the force application point of the elastic element 12 and the pivot 11 to facilitate the installation of the elastic element 12.

In some embodiments, as shown in fig. 9-11, when the crank angle is in the range of 0 to 180 degrees, the distance between the force application position of the elastic element 12 acting on the swing link 10 and the central axis of the pivot 11 is L, the elastic force of the elastic element 12 is F, the rotational inertia of the swing link 10 relative to the pivot 11 is J, and the rotational angular velocity of the swing link 10 is α, where F is greater than or equal to J α/L, so as to ensure that the slider contact portion 1002 always contacts the slider 7, i.e., to avoid the problem that the slider contact portion 1002 separates from the slider 7 due to the too fast rotation speed of the swing link 10 during the reciprocating movement of the slider 7.

In some alternative embodiments, fig. 11 shows different examples of the force application position of the elastic member 12 to the swing link 10, as indicated by three arrows in fig. 11, for example, the force application position of the elastic member 12 to the swing link 10 is located on the upper surface (upper surface in fig. 11) of the slider contact portion 1002. Optionally, the force application position of the elastic element 12 on the swing rod 10 may also be located in the middle of the rod 1001 and on the side of the rod 1001 away from the exhaust hole 2, or on the side of the rod 1001 facing the exhaust hole 2, so that the sliding piece contact portion 1002 and the sliding piece 7 are always kept in contact, and of course, the elastic element 12 may be connected to other portions of the swing rod 10 to achieve the purpose of always contacting the swing rod 10 and the sliding piece 7.

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, the discharge hole 2 is formed on the upper bearing 5, that is, 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 and 7, in some embodiments, the compression mechanism 300 further includes a lift stopper 9, the lift stopper 9 is used for limiting the lift of the exhaust valve plate 8, that is, limiting the lift of the free end 802 of the exhaust valve plate 8, the lift stopper 9 is provided with an avoidance hole 901 for avoiding the valve plate contact portion 1003, and the valve plate contact portion 1003 can pass through the avoidance hole 901 to contact with the free end 802 of the exhaust valve plate 8 to drive the exhaust valve plate 8. It should be understood that the relief hole 901 may be a circumferentially open hole or a closed hole. 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, as shown in fig. 6 and 9 to 10, the valve sheet contact part 1003 extends from the rod 1001 toward a side of the discharge hole 2. Preferably, the valve sheet contact 1003 is perpendicular to the 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 and 10, slider contact 1002 is formed by the second end of rod 1001 or a portion thereof.

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, a rocker 10, a pivot 11, and a spring. 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 slide sheet 7, when the slide sheet 7 moves outwards, the outer end of the slide sheet 7 drives the slide sheet contact part 1002 of the swing rod 10, 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.

Elastic component 12 is located between body of rod 1001 and upper bearing 5, and elastic component 12 adopts circular cone spiral compression spring, and circular cone spiral compression spring's thin end is connected with body of rod 1001, and circular cone spiral compression spring's butt is installed on upper bearing 5, and elastic component 12 has the elastic force that drive gleitbretter contact site 1002 contacts with the outer end of gleitbretter 7 all the time.

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

As shown in fig. 9 and 12, when the crank angle is 180 degrees, the sliding vane 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, the valve plate contact portion 1003 of the swing link 10 does not contact the exhaust valve plate 8, and at this time, the elastic member 12 pushes the lever upward to make the sliding vane contact portion 1002 contact the sliding vane 7 all the time. When the piston 3 continues to rotate from the 180-degree rotation angle, that is, the slide plate 7 moves from the inner limit position shown in fig. 12 to the outer limit position shown in fig. 11, the slide plate 7 drives the swing rod 10 to swing counterclockwise from the position shown in fig. 9, the valve plate contact portion 1003 contacts the exhaust valve plate 8 and drives the exhaust valve plate 8 downwards to gradually close the exhaust hole 2, and finally, the slide plate 7 moves to the outer limit position shown in fig. 11, and the valve plate contact portion 1003 of the swing rod 10 drives the exhaust valve plate 8 to completely close the exhaust hole 2.

During the whole operation process of the compression mechanism 300, the elastic force applied to the swing rod 10 by the elastic element 12 makes the slide contact portion 1002 contact the slide 7 all the time without disengaging.

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

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

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

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the present disclosure, the terms "one embodiment," "some embodiments," "an example," "a specific example," or "some examples" and the like mean that a specific feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction. Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. A compression mechanism, comprising:

the air cylinder 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 swing rod drives the swing rod to swing around a pivot when the sliding sheet moves outwards so that the swing rod pushes the exhaust valve sheet to close the exhaust hole;

and the elastic piece is used for applying elastic force to the swing rod so as to enable the swing rod to be always kept in contact with the sliding piece.

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

3. The compression mechanism of claim 1, wherein the resilient member is a coil spring, a leaf spring, or a torsion spring.

4. The compression mechanism as claimed in claim 1, wherein the elastic member is a conical helical compression spring, a thin end of the conical helical compression spring is connected with the swing link, a linear diameter of the conical helical compression spring is Φ 1, a free length of the conical helical compression spring is L3, and a middle diameter of the conical helical compression spring is Φ 2, wherein L3 is 4 mm or more and 10 mm or less, Φ 1 is 0.3 mm or more and 0.5 mm or less, Φ 2 is 3 mm or more and 6 mm or less.

5. The compression mechanism as claimed in claim 1, wherein the distance between the position of the force applied by the resilient member to the rocker and the central axis of the pivot is L, wherein L is greater than or equal to 3 mm and less than or equal to 7 mm.

6. The compressing mechanism as claimed in claim 1, wherein when the crank angle of the crankshaft is in the range of 0 to 180 degrees, the distance between the position of the resilient member exerting the force on the rocker and the central axis of the pivot is L, the resilient member has a resilient force of F, the moment of inertia of the rocker relative to the pivot is J, and the rotational angular velocity of the rocker is α, where F ≧ J α/L.

7. The compression mechanism as claimed in claim 1, wherein the elastic member has a spring constant K, where K is 0.3N/mm and 1.0N/mm.

8. The compression mechanism as claimed in claim 1, wherein said pivot is mounted on said upper bearing, a first end of said resilient member being connected to said upper bearing, and a second end of said resilient member being connected to said rocker.

9. The compression mechanism as claimed in claim 1, wherein the vent hole is plural, and the swing link is disposed corresponding to at least one vent hole.

10. The compression mechanism as claimed in claim 1, further comprising a lift limiter for limiting the lift of the exhaust valve plate and provided with an avoidance hole for avoiding the swing rod.

11. The compressing mechanism as claimed in claim 1, wherein the swing rod includes a rod, a sliding piece contact portion and a valve plate contact portion, and the sliding piece moves outward to drive the rod to swing by pushing the sliding piece contact portion, so that the valve plate contact portion drives the exhaust valve plate to close the exhaust hole.

12. A compression mechanism, comprising:

a piston;

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

an exhaust hole formed on the upper bearing, the exhaust hole communicating with the cylinder chamber;

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

the swing rod can swing around the pivot, and is linked with the sliding sheet, so that the swing rod is driven to swing to push the exhaust valve sheet to close the exhaust hole when the sliding sheet moves outwards;

and the elastic piece is arranged between the upper bearing and the oscillating bar and is used for pushing the oscillating bar to be always in contact with the sliding piece.

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

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