CN111120318B

CN111120318B - Compression mechanism, compressor with same, refrigeration cycle device and air conditioner

Info

Publication number: CN111120318B
Application number: CN201811288585.6A
Authority: CN
Inventors: 郑礼成; 吴延平
Original assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2018-10-31
Filing date: 2018-10-31
Publication date: 2022-11-15
Anticipated expiration: 2038-10-31
Also published as: CN111120318A

Abstract

The invention discloses a compression mechanism and a compressor, a refrigeration cycle device and an air conditioner with the same, wherein the compression mechanism comprises: the air cylinder is internally limited with a first working cavity and a slide sheet groove communicated with the first working cavity; the sliding sheet is arranged in the sliding sheet groove and can reciprocate along the sliding sheet groove; the rolling piston is arranged in the cylinder in a rolling manner and is hinged with the sliding sheet, and the rolling piston and the sliding sheet jointly divide the first working cavity into an air suction cavity and a compression cavity; wherein, at least one of the surfaces of the slip sheet and the rolling piston which are mutually matched is provided with a low-pressure groove, and the low-pressure groove is always communicated with the air suction cavity and is always separated from the compression cavity. According to the compression mechanism provided by the embodiment of the invention, the sliding sheet can be ensured to be in close contact with the rolling piston so as to avoid collision or air pressure leakage between the sliding sheet and the rolling piston, the noise in the operation process is low, and the performance of the compression mechanism is good.

Description

Compression mechanism, compressor with same, refrigeration cycle device and air conditioner

Technical Field

The invention relates to the technical field of air compression, in particular to a compression mechanism, a compressor with the compression mechanism, a refrigeration cycle device and an air conditioner.

Background

The compression mechanism is characterized in that a sliding vane spring is not required to be arranged on the back of the sliding vane, the problem of abrasion reliability caused by line contact of the sliding vane and the roller of the traditional rolling rotor compressor can be solved, and meanwhile, friction loss is improved. However, under some working conditions, the contact position between the slide and the roller is unstable, and although the slide and the roller are hinged, they cannot be separated, but a gap is formed between the slide and the roller, and a small collision still occurs, so that a large noise is generated and air pressure leakage is easily caused.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides a compression mechanism which has low noise and good compression performance in the operation process.

The invention also provides a compressor, a refrigeration cycle device and an air conditioner with the compression mechanism.

A compression mechanism according to an embodiment of a first aspect of the present invention includes: the air cylinder is internally provided with a first working cavity and a slide sheet groove communicated with the first working cavity; the sliding sheet is arranged in the sliding sheet groove and can reciprocate along the sliding sheet groove; the rolling piston is arranged in the cylinder in a rolling manner and is hinged with the sliding sheet, and the rolling piston and the sliding sheet jointly divide the first working cavity into an air suction cavity and a compression cavity; and at least one of the surfaces of the sliding sheet and the rolling piston which are mutually matched is provided with a low-pressure groove, and the low-pressure groove is always communicated with the air suction cavity and is always separated from the compression cavity.

According to the compression mechanism provided by the embodiment of the invention, the sliding sheet can be ensured to be in close contact with the rolling piston so as to avoid collision or air pressure leakage between the sliding sheet and the rolling piston, the noise in the operation process is low, and the performance of the compression mechanism is good.

In addition, the compression mechanism according to the above embodiment of the present invention may further have the following additional technical features:

according to some embodiments of the invention, the rolling piston is provided with a hinge hole, the slide having a hinge head fitting in the hinge hole.

According to some embodiments of the invention, at least one of the surfaces of the sliding vane cooperating with the rolling piston is provided with a communication groove, the low pressure groove communicating with the suction chamber through the communication groove.

According to some embodiments of the invention, the low pressure groove and the communication groove are both provided on an inner surface of the hinge hole.

According to some embodiments of the present invention, the low pressure groove penetrates the rolling piston in a direction parallel to a central axis of the rolling piston, and the communication groove is formed by chamfering at least one end of the hinge hole.

According to some embodiments of the invention, in the cross section of the compression mechanism, the radius of the hinge joint is r, the central angle of the area of the low-pressure groove adjacent to the compression cavity, which is in contact with the hinge hole, relative to the center of the hinge joint is theta, and r theta is greater than or equal to 1mm.

According to some embodiments of the invention, the low pressure groove and the communication groove are both provided on an outer surface of a hinge joint of the sliding piece.

According to some embodiments of the invention, the low pressure groove extends in a direction parallel to a central axis of the joint, and the communication groove extends in a circumferential direction of the joint.

According to some embodiments of the invention, the side wall of the slide facing the compression chamber is configured as a plane and the plane is tangential to the hinge joint.

According to some embodiments of the invention, in the cross-section of the compression mechanism, a portion of the inner surface of the hinge hole from the low pressure groove to the compression chamber is configured as an arc-shaped wall and a straight wall, the straight wall is tangent to the arc-shaped wall and the hinge is engaged with the arc-shaped wall.

According to some embodiments of the present invention, a distance between a center of the rolling piston and a center of the first working chamber is e, a distance between a center of the hinge hole and a center of the rolling piston is L, an included angle between the plane of the vane and the straight wall is α, and α is greater than or equal to arcsin (e/L) when a length of the vane extending from the vane groove is maximum.

According to some embodiments of the invention, the maximum depth of the low pressure groove is 0.2mm or more and 2mm or less; and/or the maximum depth of the communication groove is more than or equal to 0.2mm and less than or equal to 2mm.

According to some embodiments of the invention, the low pressure groove is located closer to the compression chamber than to the suction chamber when the length of the vane extending from the vane groove is a maximum.

According to some embodiments of the invention, the cylinder further defines a mounting groove in communication with the vane groove, the mounting groove being located at an end of the vane groove remote from the first working chamber, a valve plate being disposed in the mounting groove, the vane and the valve plate defining a second working chamber in the vane groove.

A compressor according to an embodiment of the second aspect of the present invention includes the compression mechanism according to the embodiment of the first aspect of the present invention.

According to the compressor provided by the embodiment of the invention, by utilizing the compression mechanism provided by the embodiment of the first aspect of the invention, the noise is low in the operation process and the compression performance is good.

A refrigeration cycle apparatus according to an embodiment of the third aspect of the invention includes the compressor according to the embodiment of the second aspect of the invention.

According to the refrigeration cycle device provided by the embodiment of the invention, by utilizing the compressor provided by the embodiment of the second aspect of the invention, the noise generated in the operation process can be effectively reduced, and the refrigeration effect is better.

An air conditioner according to an embodiment of the fourth aspect of the present invention includes the refrigeration cycle apparatus according to the embodiment of the third aspect of the present invention.

According to the air conditioner provided by the embodiment of the invention, by utilizing the refrigeration cycle device provided by the embodiment of the third aspect of the invention, the noise in the operation process is low, the refrigeration or heating effect is good, and the use experience of a user is improved.

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

Drawings

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

fig. 1 is a schematic structural view of a compression mechanism in the related art;

FIG. 2 is a diagram illustrating a force state of a sliding vane when a crank angle of a compression mechanism in the related art is rotated from 90 to 180;

FIG. 3 is a diagram illustrating a force state of a sliding vane when a crank angle of a compression mechanism in the related art is rotated from 180 to 270;

FIG. 4 is a graph showing a relationship between a contact force applied to a vane of a compression mechanism and a crank angle in the related art;

FIG. 5 is a schematic structural view of a compression mechanism according to some embodiments of the invention;

FIG. 6 isbase:Sub>A schematic cross-sectional view of the rolling piston of FIG. 5 taken along the line A-A;

FIG. 7 is a force state diagram of a sliding vane of a compression mechanism according to some embodiments of the present invention;

FIG. 8 is a schematic diagram of a compression mechanism according to further embodiments of the present invention;

FIG. 9 is a schematic illustration of a slider of a compression mechanism according to further embodiments of the present invention;

FIG. 10 is a schematic illustration of a slider for a compression mechanism according to further embodiments of the present invention;

fig. 11 is a schematic structural view of a compressor according to an embodiment of the present invention;

fig. 12 is an operational principle diagram of a refrigeration cycle device according to an embodiment of the present invention.

Reference numerals:

the related technology comprises the following steps: a compression mechanism 100'; a cylinder 10'; a first working chamber 11'; the suction chamber 11a'; the compression chamber 11b'; a slide groove 12'; a slide 20'; a head portion 21'; a roller 30'; hinge holes 31';

the invention comprises the following steps: a compression mechanism 100;

a cylinder 10; first air-intake holes 10a; a first exhaust hole 10b; a first working chamber 11; a suction chamber 11a; a compression chamber 11b; a slide groove 12; a mounting groove 13; a valve plate 14; a second working chamber 15;

a slip sheet 20; the side wall 20a of the slide facing the compression chamber; a hinge joint 21; a neck-reducing portion 22; a slide portion 23;

a rolling piston 30; a hinge hole 31; the arc-shaped wall 31a; the flat wall 31b;

a low pressure tank 40; a communication groove 41;

a compressor 200; a refrigeration cycle device 300; an outdoor heat exchanger 310; a first throttling element 320; a flash evaporator 330; a second throttling element 340; an indoor heat exchanger 350; four-way valve 360.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "center", "length", "width", "thickness", "upper", "lower", "left", "right", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be considered limiting. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.

The compression mechanism 100' in the related art is described below with reference to fig. 1 to 4.

In the related art, a compression mechanism 100' is proposed, in which a head 21' of a vane 20' is connected to a roller 30' in a hinge manner, so that there is no need to provide a vane spring on a back of the vane 20', and a problem of wear reliability due to linear contact between the vane 20' and the roller 30' of a rolling rotor compressor can be solved, and friction loss is also improved.

As shown in fig. 1, the roller 30' is provided with a hinge hole 31' communicating with the first working chamber 11', and the cylindrical head 21' of the slide 20' is engaged with the hinge hole 31' to realize the hinge, so that the head 21' of the slide 20' is not separated from the hinge hole 31' of the roller 30' during the reciprocating motion of the slide 20 '. The roller 30' cooperates with the eccentric portion of the crankshaft to drive the roller 30' to rotate eccentrically within the cylinder 10', the crankshaft rotates in a counterclockwise direction in the orientation shown in fig. 1, and the center of rotation of the crankshaft coincides with the center of the center hole of the cylinder 10', the center of the roller 30' and the center of rotation being eccentric by an amount e. A first working chamber 11' is defined between the central hole of the cylinder 10' and the outer diameter of the roller 30', the first working chamber 11' is divided into a suction chamber 11a ' and a compression chamber 11b ' by the sliding vane 20', the roller 30' is driven by the crankshaft to swing around the center of the head 21' of the sliding vane 20', the volume of the suction chamber 11a ' is increased continuously, and a refrigerant is sucked; meanwhile, the volume of the compression cavity 11b 'is continuously reduced, the refrigerant is compressed in the compression cavity 11b', and when the pressure is increased to the exhaust pressure, an exhaust valve on a bearing or a partition plate on the end surface is opened to discharge the refrigerant. The connection of the head 21 'of the slide 20' to the body is provided with a constriction to avoid interference of the roller 30 'with the two side walls of the slide 20' during operation.

The force analysis of the slide 20' is now carried out with reference to figures 2-4, as shown in figure 2 in relation to the contact force to which the head 21' of the slide 20' is subjected. The trailing portion of the sliding vane 20 'is subjected to a high back pressure Pd, the portion of the sliding vane 20' exposed to the suction chamber 11a 'is subjected to a suction pressure Ps, and the portion of the compression chamber 11b' is subjected to a compression chamber 11b 'pressure Pv, the hinge portion of the leading portion 21' of the sliding vane 20 'is in clearance fit with the hinge hole 31', and the gas force can be considered as a linear transition pressure along the clearance passage from the outlet Ps of the suction chamber 11a 'to the outlet Pv of the compression chamber 11 b'. Further, the vane 20' is also subjected to a frictional force F ' of the vane slot 12' opposite to the moving direction of the vane 20' and an inertial force F ' opposite to the direction of acceleration. Now, when the length of the sliding vane 20' extending from the sliding vane slot 12' is shortest, that is, the rotation angle of the crankshaft is 0 when the eccentric direction of the crankshaft is opposite to the sliding vane slot 12', as shown in fig. 2, the sliding vane 20' performs deceleration motion when the rotation angle of the crankshaft is from 90 ° to 180 °, and the inertia force F ' borne by the sliding vane 20' faces the roller 30'; as shown in FIG. 3, when the angle of rotation of the crankshaft is from 180 to 270, the vane 20 'is accelerated, and the inertial force F' applied to the vane 20 'is directed toward the roller 30'.

Referring to fig. 4, the relationship between the magnitude of the contact force applied to the vane 20' and the rotational angle of the crankshaft will be described, wherein a positive value of the contact force indicates that the vane 20' is under a pressure, i.e. the vane 20' and the roller 30' approach each other, and a negative value of the contact force indicates that the vane 20' is under a tension, i.e. the vane 20' and the roller 30' move away from each other. When the crank angle is close to 180 °, the slide 20' and the roller 30' are most likely to separate, and with reference to fig. 2, because there is a gap between the head 21' of the slide 20' and the hinge hole 31', when the contact force between the slide 20' and the roller 30' is switched between the pressure force and the pull force, the two are likely to collide, thereby increasing the noise of the compressor, and at the same time, the change of the gap between the head 21' of the slide 20' and the hinge hole 31' may also cause the increase of the air pressure leakage from the compression cavity 11b ' to the suction cavity 11a ' through the gap, thereby affecting the performance of the compression mechanism 100'.

In consideration of the above-mentioned related art in which the contact position of the vane 20 'and the roller 30' is unstable, and there is a gap therebetween and a slight collision occurs, thereby generating noise or air pressure leakage, the present invention proposes a compression mechanism 100, and a compressor 200, a refrigeration cycle device 300, and an air conditioner having the same.

A compression mechanism 100 according to an embodiment of the first aspect of the present invention is described below with reference to fig. 5 to 11.

As shown in fig. 5, a compression mechanism 100 according to an embodiment of the present invention includes a cylinder 10, a sliding vane 20, and a rolling piston 30, wherein the cylinder 10 defines a first working chamber 11 and a sliding vane groove 12 communicated with the first working chamber 11, the sliding vane 20 is disposed in the sliding vane groove 12 and can reciprocate along the sliding vane groove 12, the rolling piston 30 is rollably disposed in the cylinder 10 and is hinged to the sliding vane 20, the rolling piston 30 and the sliding vane 20 jointly divide the first working chamber 11 into a suction chamber 11a and a compression chamber 11b, wherein at least one of surfaces of the sliding vane 20 and the rolling piston 30, which are engaged with each other, is provided with a low pressure groove 40, and the low pressure groove 40 is always communicated with the suction chamber 11a and is always separated from the compression chamber 11b.

Specifically, a first working chamber 11 is defined in the cylinder 10, the sliding vane 20 is hinged to the rolling piston 30 so that the rolling piston 30 drives the sliding vane 20 to reciprocate in the sliding vane slot 12 during rolling in the first working chamber 11, the sliding vane 20 and the rolling piston 30 together divide the first working chamber 11 into a suction chamber 11a and a compression chamber 11b, the cylinder 10 has a first suction hole 10a communicated with the suction chamber 11a and a first discharge hole 10b communicated with the compression chamber 11b, and refrigerant enters the suction chamber 11a from the first suction hole 10a, is then compressed by the first compression chamber 11b along with the rolling of the first rolling piston 30 and is discharged from the first discharge hole 10 b.

It should be noted that the low pressure groove 40 may be disposed on a surface of the sliding vane 20 contacting the rolling piston 30, or on a surface of the rolling piston 30 contacting the sliding vane 20, or on both the sliding vane 20 and the rolling piston 30, and during the rolling process of the rolling piston 30 in the first working chamber 11, the low pressure groove 40 is always in communication with the suction chamber 11a, and the low pressure groove 40 is always in a separated state from the compression chamber 11b, the pressure of the portion of the sliding vane 20 exposed from the low pressure groove 40 and the suction chamber 11a is equal to the pressure of the suction chamber 11a, and the pressure of the portion of the sliding vane 20 exposed from the compression chamber 11b is equal to the pressure of the compression chamber 11b, so that, as shown in fig. 7, the gas acting force applied to the sliding vane 20 is equal to the resultant force of the pressure in the suction chamber 11a to the portion of the sliding vane 20 exposed from the low pressure groove 40 and the suction chamber 11a and the pressure of the pressure in the compression chamber 11b to the portion of the sliding vane 20 exposed from the compression chamber 11b. It should be noted that, since the gas pressure inside the suction chamber 11a is much lower than the gas pressure inside the compression chamber 11b, the greater the surface area of the slide 20 exposed to the suction chamber 11a and the low-pressure groove 40 relative to the surface area of the slide 20 exposed to the compression chamber 11b, the smaller the force of the gas on the slide 20.

According to the compression mechanism 100 of the embodiment of the invention, the low-pressure groove 40 communicated with the air suction cavity 11a is defined between the sliding vane 20 and the rolling piston 30, the pressure value in the low-pressure groove 40 is the same as the pressure value in the air suction cavity 11a, so that the air pressure borne by the area of the head of the sliding vane 20 between the low-pressure groove 40 and the air suction cavity 11a is the same as the air pressure in the air suction cavity 11a, and the average value of the transition pressure of the area of the head of the sliding vane 20 between the low-pressure groove 40 and the compression cavity 11b is correspondingly reduced, thereby greatly reducing the gas acting force of the head of the sliding vane 20, ensuring that the sliding vane 20 is always pressed on the rolling piston 30 in the operation process, avoiding the noise problem caused by the collision between the sliding vane 20 and the rolling piston 30, and effectively reducing the leakage at the head of the sliding vane 20, thereby improving the performance of the compressor 200.

Therefore, according to the compression mechanism 100 of the embodiment of the present invention, the sliding vane 20 can be ensured to be in close contact with the rolling piston 30 to avoid collision or air pressure leakage between the sliding vane 20 and the rolling piston 30, noise during operation is low, and the performance of the compression mechanism 100 is good.

In some embodiments of the present invention, as shown in fig. 5, the rolling piston 30 is provided with a hinge hole 31, and the sliding piece 20 has a hinge 21, and the hinge 21 is fitted in the hinge hole 31. Specifically, at least a portion of the hinge hole 31 is circular, and an end of the slide 20 facing the rolling piston 30 is configured with a cylindrical hinge joint 21, and the hinge joint 21 is fitted into the hinge hole 31 to hinge the slide 20 with the rolling piston 30, whereby it is possible to ensure that the slide 20 is rotatable with respect to the rolling piston 30 without being separated from the rolling piston 30.

Preferably, the hinge joint 21 is coaxially disposed with the hinge hole 31 and is tightly fitted, so that the outer surface of the hinge joint 21 and the inner surface of the hinge hole 31 can be in tight contact to separate the suction chamber 11a from the compression chamber 11b, and the compressed air in the compression chamber 11b is prevented from leaking to the suction chamber 11a through the gap between the hinge joint 21 and the hinge hole 31, thereby ensuring the performance of the compression mechanism 100 and the operation of the compression mechanism 100 is stable.

In some embodiments of the invention, with continued reference to the embodiment shown in fig. 5, at least one of the surfaces of the sliding piece 20 cooperating with the rolling piston 30 is provided with a communication groove 41, the low-pressure groove 40 communicating with the suction chamber 11a through the communication groove 41. Specifically, the communication groove 41 is a closed channel defined by the sliding piece 20 and the rolling piston 30 and used for communicating the low pressure groove 40 with the air suction cavity 11a, the communication groove 41 may be disposed on an outer surface of the sliding piece 20 in contact with the rolling piston 30, or on an inner surface of the rolling piston 30 in contact with the sliding piece 20, or on both the sliding piece 20 and the rolling piston 30, and in a cross section of the compression mechanism 100, one end of the communication groove 41 is communicated with the low pressure groove 40 and extends in a direction of the air suction cavity 11a along a circumferential direction of the hinge joint 21, so that the sliding piece 20 rotates to any angle relative to the rolling piston 30, and the communication between the low pressure groove 40 and the air suction cavity 11a can be ensured.

According to some embodiments of the present invention, as shown in FIGS. 5 and 8, when the length of the vane 20 extending from the vane slot 12 is the largest, the low pressure slot 40 is located closer to the compression chamber 11b than to the suction chamber 11 a. That is, when the slide plate 20 is moved to the maximum length protruding into the first working chamber 11, the low pressure groove 40 is located at the side close to the compression chamber 11b of the central plane passing through the axial direction of the slide plate 20, so that the exposed area of the hinge joint 21 in the communication groove 41 and the low pressure groove 40 is larger than the exposed area of the hinge joint 21 in the compression chamber 11b, and since the air pressure in the suction chamber 11a is lower than the air pressure in the compression chamber 11b, the gas acting force applied to the hinge joint 21 can be further reduced.

In some specific examples of the present invention, as shown in fig. 5 to 7, both the low pressure groove 40 and the communication groove 41 are provided on the inner surface of the hinge hole 31. Specifically, the low pressure groove 40 and the communication groove 41 are formed by the inner surface of the hinge hole 31 being depressed inward, and the outer surface of the hinge head 21 closes the opening of the low pressure groove 40 and forms a closed passage with the communication groove 41 communicating the low pressure groove 40 with the suction chamber 11 a.

Alternatively, as shown in fig. 6, the low pressure groove 40 penetrates the rolling piston 30 in a direction parallel to the central axis of the rolling piston 30, and the communication groove 41 is formed by chamfering at least one end of the hinge hole 31.

Specifically, the low pressure groove 40 has a length direction parallel to the central axis of the rolling piston 30, the low pressure groove 40 penetrates both end surfaces of the rolling piston 30, the communication groove 41 is formed by chamfering the end surface of the rolling piston 30 toward the inner surface of the hinge hole 31, and the communication groove 41 extends from the low pressure groove 40 to a side of the opening of the hinge hole 31 adjacent to the suction chamber 11a in the circumferential direction of the hinge hole 31, whereby the low pressure groove 40 and the communication groove 41 can be easily processed. Preferably, the two communicating grooves 41 are respectively formed at two circumferential ends of the hinge hole 31, so that the low pressure groove 40 and the suction chamber 11a can be effectively communicated with each other, and the air pressure received by the portion of the sliding piece 20 exposed from the low pressure groove 40 can be ensured to be equal to the air pressure received by the suction chamber 11 a.

Further, as shown in FIG. 5, in the cross section of the compressing mechanism 100, the radius of the hinge joint 21 is r, and on the side of the low pressure groove 40 adjacent to the compressing chamber 11b, the central angle of the area where the hinge joint 21 contacts the hinge hole 31 with respect to the center of the hinge joint 21 is θ, and r θ ≧ 1mm. In other words, on the side of the low pressure groove 40 in the counterclockwise direction around the joint 21, the projection of the area where the joint 21 and the joint hole 31 contact is an arc in the cross section, and the central angle of the arc is θ, where r θ is equal to or greater than 1mm, that is, the arc length of the arc is equal to or greater than 1mm, thereby ensuring that the sealing distance between the low pressure groove 40 and the compression chamber 11b is large, and improving the sealing property between the low pressure groove 40 and the compression chamber 11b.

In other specific examples of the present invention, as shown in fig. 8 and 9, the low pressure groove 40 and the communication groove 41 are provided on the outer surface of the hinge joint 21 of the slide sheet 20. Specifically, the low pressure groove 40 and the communication groove 41 are formed by the outer surface of the hinge head 21 being depressed inward, and the inner surface of the hinge hole 31 closes the opening of the low pressure groove 40 and forms a closed passage with the communication groove 41 communicating the low pressure groove 40 with the suction chamber 11 a.

Alternatively, as shown in fig. 9, the low-pressure groove 40 extends in a direction parallel to the center axis of the joint 21, and the communication groove 41 extends in the circumferential direction of the joint 21.

Specifically, the length direction of the low pressure groove 40 is parallel to the central axis of the rolling piston 30, the low pressure groove 40 penetrates through two end faces of the hinge joint 21, the communication groove 41 is formed in the outer surface of the hinge joint 21, and the communication groove 41 extends from the low pressure groove 40 towards one side of the hinge joint 21 adjacent to the air suction cavity 11a along the circumferential direction of the hinge joint 21, so that the communication groove 41 and the low pressure groove 40 are conveniently machined, and in the process that the hinge joint 21 rotates in the hinge hole 31, the low pressure groove 40 and the air suction cavity 11a are always kept in a communication state through the communication groove 41. It should be noted that, in other embodiments of the present invention, the low pressure groove 40 may not penetrate through both ends of the hinge joint 21, so that the sealing performance of the low pressure groove 40 may be further improved to prevent gas leakage.

It should be noted that, since the low pressure groove 40 and the communication groove 41 are disposed in the hinge joint 21 of the sliding vane 20, the sealing distance between the low pressure groove 40 and the compression chamber 11b varies with the swing of the rolling piston 30, and when the crank angle is 90 degrees, the sealing distance is the smallest, and at this time, the swing angle of the rolling piston 30, that is, the included angle between the connecting line between the center of the rolling piston 30 and the center of the hinge hole 31 and the sliding vane groove 12 is β = arcsin (e/L), where e is the distance between the center of the rolling piston 30 and the center of the cylinder 10, and L is the distance between the center of the hinge hole 31 and the center of the rolling piston 30. In order to ensure that the minimum sealing distance between the low-pressure groove 40 and the compression cavity 11b is greater than 1mm, r (theta-beta) = r [ theta-arcsin (e/L) ] > is greater than or equal to 1mm.

According to some embodiments of the invention, as shown in fig. 10, the side wall 20a of the slide facing the compression chamber is configured as a plane and the plane is tangential to the hinge joint 21.

It should be noted that, in some embodiments shown in fig. 5 to 9, the sliding piece 20 includes a sliding portion 23, a constricted portion 22 and a joint 21, the constricted portion 22 has a width smaller than that of the sliding portion 23 and a diameter of the joint 21, so that an end surface of the sliding portion 23 located on a side of the compression chamber 11b facing the rolling piston 30 is subjected to an upward pressure Pv, thereby reducing a contact force between the joint 21 and the joint hole 31 and affecting a sealing performance between the low pressure groove 40 and the compression chamber 11b. In the embodiment shown in fig. 10, in the portion of the sliding vane 20 located in the compression chamber 11b, the distance between the right side wall of the constricted portion 22 and the central axis of the sliding vane 20 is equal to the distance between the right side wall of the sliding portion 23 and the central axis of the sliding vane 20, that is, the right side wall of the constricted portion 22 and the right side wall of the sliding portion 23 are located in the same plane, and the right side wall of the constricted portion 22 is tangent to the outer surface of the hinge joint 21, so that the sliding portion 23 is prevented from being subjected to the upward pressure Pv, the contact force between the hinge joint 21 and the hinge hole 31 is increased, and the sealing effect between the low pressure groove 40 and the compression chamber 11b is improved.

In a further example of the present invention, with continued reference to the embodiment shown in fig. 10, in the cross section of the compression mechanism 100, the portion of the inner surface of the hinge hole 31 from the low pressure groove 40 to the compression chamber 11b is configured as an arc-shaped wall 31a and a straight wall 31b, the straight wall 31b is tangent to the arc-shaped wall 31a and the hinge joint 21 is engaged with the arc-shaped wall 31 a. Specifically, the inner surface of the hinge hole 31 includes an arc-shaped wall 31a and a straight wall 31b connected in sequence in a direction from the low pressure groove 40 to the compression chamber 11b, wherein the arc-shaped wall 31a cooperates with the hinge 21 to separate the low pressure groove 40 from the compression chamber 11b, and the straight wall 31b is tangent to the arc-shaped wall 31a and has an angle with the side wall 20a of the slider facing the compression chamber, whereby the straight wall 31b can be prevented from interfering with the rotation of the hinge 21 in the hinge hole 31. Preferably, since the opening of the hinge hole 31 is large, the straight wall 31b may be processed using a grinding process, whereby the processing difficulty is greatly reduced.

Optionally, the distance between the center of the rolling piston 30 and the center of the first working chamber 11 is e, the distance between the center of the hinge hole 31 and the center of the rolling piston 30 is L, the included angle between the plane of the sliding vane 20 and the straight wall 31b is α, and α ≧ arcsin (e/L) when the length of the sliding vane 20 extending from the sliding vane slot 12 is maximum. Therefore, in the process of left-right swinging of the rolling piston 30, interference between the straight wall 31b of the hinge hole 31 and the sliding piece 20 can be better avoided, and the hinge effect of the sliding piece 20 and the hinge hole 31 is better.

According to some embodiments of the present invention, the maximum depth of the low pressure groove 40 is 0.2mm or more and 2mm or less; and/or the maximum depth of the communication groove 41 is not less than 0.2mm and not more than 2mm. As shown in fig. 5, 8, and 10, the maximum depth w of the low-pressure groove 40 is equal to the maximum depth w of the communication groove 41, and both the maximum depth w of the low-pressure groove 40 and the maximum depth w of the communication groove 41 are equal to or greater than 0.2mm and equal to or less than 2mm. It should be noted that if w is less than 0.2mm, the difficulty of the processing technique of the low-pressure groove 40 and the communication groove 41 is large, and the communication effect between the low-pressure groove 40 and the suction cavity 11a is difficult to ensure; if w is greater than 2mm, the structural strength of the low pressure groove 40 and the communication groove 41 is poor, and damage is easily caused in the case of high frequency operation of the slider 20, and therefore, the maximum depth w of the low pressure groove 40 and the communication groove 41 is required to be greater than or equal to 0.2mm and less than or equal to 2mm.

According to some embodiments of the present invention, as shown in fig. 11, the cylinder 10 further defines a mounting groove 13 communicated with the vane groove 12, the mounting groove 13 is located at an end of the vane groove 12 far from the first working chamber 11, a valve plate 14 is disposed in the mounting groove 13, and the vane 20 and the valve plate 14 define a second working chamber 15 in the vane groove 12.

Specifically, both end surfaces of the cylinder 10 in the axial direction are sealed by an upper bearing and a lower bearing, respectively, and the valve plate 14 is provided with a second air intake hole, an air intake valve sheet for opening and closing the second air intake hole, a second air discharge hole, and an air discharge valve sheet for opening and closing the second air discharge hole. In the process that the rolling piston 30 rolls, the sliding vane 20 reciprocates in the sliding vane groove 12, when the sliding vane 20 moves in the direction towards the first working chamber 11, the volume of the second working chamber 15 is gradually increased, when the air pressure in the second working chamber 15 is reduced to a certain degree, the air suction valve plate is opened, and the second working chamber 15 sucks a medium-pressure refrigerant through a second air suction hole; when the slide sheet 20 moves towards the direction far away from the first working chamber 11, the volume of the second working chamber 15 is gradually reduced, the refrigerant in the second working chamber 15 is compressed, and when the air pressure in the second working chamber 15 is increased to a certain degree, the exhaust valve plate is opened to discharge the high-pressure refrigerant through the second exhaust hole. In this way, by adopting the structure of the double working chambers, the working efficiency of the compression mechanism 100 can be improved, so that the cooling or heating effect is improved, and the user experience is better.

A compressor 200 according to an embodiment of the second aspect of the present invention is described below with reference to fig. 11.

A compressor 200 according to an embodiment of the second aspect of the present invention, as shown in fig. 11, includes a compression mechanism 100 according to an embodiment of the first aspect of the present invention. It is to be noted that the compressor 200 according to the embodiment of the second aspect of the present invention can constitute a single cylinder compressor 200 having one cylinder 10 or a multi-cylinder compressor 200 having two or more cylinders 10 by using the compression mechanism 100 according to the embodiment of the first aspect of the present invention.

According to the compressor 200 of the embodiment of the present invention, by using the compression mechanism 100 according to the embodiment of the first aspect of the present invention, noise during operation is small and compression performance is good.

A refrigeration cycle device 300 according to an embodiment of the third aspect of the invention is described below with reference to fig. 12.

As shown in fig. 12, a refrigeration cycle apparatus 300 according to an embodiment of the third aspect of the present invention includes a compressor 200 according to an embodiment of the second aspect of the present invention.

According to the refrigeration cycle device 300 of the embodiment of the invention, by using the compressor 200 of the embodiment of the second aspect of the invention, the noise generated during the operation of the refrigeration cycle device 300 can be effectively reduced, and the refrigeration effect is good.

In some embodiments of the present invention, as shown in fig. 12, the refrigeration cycle device 300 includes: a compressor 200, a four-way valve 360, an outdoor heat exchanger 310, a first throttling element 320, a flash evaporator 330, a second throttling element 340, and an indoor heat exchanger 350. When the four-way valve 360 is in the state shown in the figure, the refrigeration apparatus is in a refrigeration mode, the high-pressure refrigerants compressed by the first working chamber 11 and the second working chamber 15 are mixed inside the compressor 200 or outside the compressor 200, and then flow to the outdoor heat exchanger 310 together for condensation, the condensed liquid refrigerants are throttled to a required intermediate pressure by the first throttling element 320, then are separated in the flash evaporator 330, the separated saturated liquid refrigerants enter the second throttling element 340 for throttling, and finally reach an evaporation pressure value and enter the indoor heat exchanger 350 for evaporation. The evaporated refrigerant passes through the first suction holes 10a and returns to the first working chamber 11 again for compression, and the intermediate-pressure gas separated in the flash evaporator 330 returns to the second working chamber 15 again through the second suction holes for compression.

The work of refrigerant throttling expansion in the refrigeration cycle device in the related art is completely wasted, and the intermediate pressure gas separated by the flash evaporator 330 in the refrigeration cycle device 300 of the invention directly returns to the second working chamber 15 for compression, which is equivalent to recycling a part of expansion work. In addition, since the refrigerant entering the indoor heat exchanger 350 is a saturated liquid refrigerant, the dryness of the refrigerant in the indoor heat exchanger 350 is reduced, and thus the heat exchange efficiency of the indoor heat exchanger 350 is improved.

The refrigeration cycle device 300 is switchable into a heating mode through the four-way valve 360, at the moment, high-pressure refrigerants compressed by the first working cavity 11 and the second working cavity 15 flow to the indoor heat exchanger 350 together for condensation, liquid refrigerants after condensation are throttled to required intermediate pressure through the throttling element and then separated in the flash evaporator 330, saturated liquid refrigerants after separation enter the throttling element again for throttling, and finally, an evaporation pressure value is reached and the refrigerant enters the outdoor heat exchanger 310 for evaporation. The evaporated refrigerant passes through the first suction hole 10a and returns to the first working chamber 11 again to be compressed. The intermediate-pressure gas separated in the flash evaporator 330 returns to the second working chamber 15 through the second suction hole to be compressed. Therefore, under the condition of large indoor and outdoor temperature difference, the heating capacity of the refrigeration cycle system in the embodiment of the third aspect of the invention in a low-temperature environment is greatly improved, the heating effect is good, and the user experience is improved.

An air conditioner according to a fourth aspect embodiment of the present invention includes the refrigeration cycle device 300 according to the third aspect embodiment of the present invention.

According to the air conditioner of the embodiment of the present invention, by using the refrigeration cycle apparatus 300 according to the embodiment of the third aspect of the present invention, noise is low during operation, the cooling or heating effect is good, and the user experience is improved.

Other constitutions and operations of the compression mechanism 100 and the compressor 200 having the same, the refrigeration cycle device 300 and the air conditioner having the same according to the embodiment of the present invention are known to those of ordinary skill in the art and will not be described in detail herein.

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

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A compression mechanism, comprising:

the air cylinder is internally provided with a first working cavity and a slide sheet groove communicated with the first working cavity;

the sliding sheet is arranged in the sliding sheet groove and can reciprocate along the sliding sheet groove;

the rolling piston is arranged in the cylinder in a rolling mode and is hinged with the sliding sheet, and the rolling piston and the sliding sheet jointly divide the first working cavity into an air suction cavity and a compression cavity;

and at least one of the surfaces of the sliding sheet and the rolling piston which are mutually matched is provided with a low-pressure groove, and the low-pressure groove is always communicated with the air suction cavity and is always separated from the compression cavity.

2. The compression mechanism as claimed in claim 1, wherein the rolling piston is provided with a hinge hole, and the sliding piece has a hinge head fitted in the hinge hole.

3. The compressing mechanism as set forth in claim 2, wherein at least one of the surfaces of the sliding piece and the rolling piston cooperating with each other is provided with a communicating groove, and the low pressure groove communicates with the suction chamber through the communicating groove.

4. The compressing mechanism as set forth in claim 3, wherein said low pressure groove and said communicating groove are formed in an inner surface of said hinge hole.

5. The compression mechanism according to claim 4, wherein the low pressure groove penetrates the rolling piston in a direction parallel to a central axis of the rolling piston, and the communication groove is formed by chamfering at least one end of the hinge hole.

6. The compression mechanism as claimed in claim 4, wherein in the cross section of the compression mechanism, the radius of the hinge head is r, the central angle of the area of the low pressure groove adjacent to the compression chamber, which is in contact with the hinge hole, relative to the center of the hinge head is θ, and r θ is greater than or equal to 1mm.

7. The compressing mechanism as claimed in claim 3, wherein the low pressure groove and the communicating groove are both provided on an outer surface of the hinge of the sliding piece.

8. The compression mechanism as claimed in claim 7, wherein the low pressure groove extends in a direction parallel to a central axis of the joint, and the communication groove extends in a circumferential direction of the joint.

9. The compression mechanism as in any one of claims 2-8, wherein a sidewall of the slide facing the compression chamber is configured as a plane tangential to the hinge.

10. The compression mechanism of claim 9, wherein, in a cross-section of the compression mechanism, a portion of the inner surface of the hinge bore from the low pressure groove to the compression chamber is configured as an arcuate wall and a flat wall, the flat wall being tangent to the arcuate wall and the hinge joint engaging the arcuate wall.

11. The compression mechanism as claimed in claim 10, wherein a distance between a center of the rolling piston and a center of the first working chamber is e, a distance between a center of the hinge hole and a center of the rolling piston is L, an angle between the plane of the vane and the straight wall is α, and α ≧ arcsin (e/L) when a length of the vane protruding from the vane groove is maximized.

12. The compression mechanism according to any one of claims 3 to 8, wherein the maximum depth of the low-pressure groove is 0.2mm or more and 2mm or less; and/or

The maximum depth of the communicating groove is more than or equal to 0.2mm and less than or equal to 2mm.

13. The compression mechanism as recited in any one of claims 1-8 wherein said low pressure groove is positioned closer to said compression chamber than said suction chamber when said slide extends a maximum length from said slide groove.

14. The compression mechanism as recited in any one of claims 1-8 wherein said cylinder further defines a mounting slot in communication with said vane slot, said mounting slot located at an end of said vane slot remote from said first working chamber, a valve plate disposed within said mounting slot, said vane and said valve plate defining a second working chamber within said vane slot.

15. A compressor characterized by comprising the compression mechanism according to any one of claims 1 to 14.

16. A refrigeration cycle apparatus, characterized by comprising the compressor according to claim 15.

17. An air conditioner characterized by comprising the refrigeration cycle device according to claim 16.