CN106593870B

CN106593870B - Rotary compressor and refrigeration system with same

Info

Publication number: CN106593870B
Application number: CN201611110293.4A
Authority: CN
Inventors: 汤立宽; 巫华龙; 杨国用
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2016-12-06
Filing date: 2016-12-06
Publication date: 2020-05-22
Anticipated expiration: 2036-12-06
Also published as: CN106593870A

Abstract

The invention discloses a rotary compressor and a refrigeration system with the same, wherein a shell is internally provided with an electric motor and a compression mechanism part, the compression mechanism part comprises at least one group of variable-capacity air cylinder assemblies, and the variable-capacity air cylinder assemblies comprise: the variable-capacity air cylinder is provided with a variable-capacity slide sheet groove, a variable-capacity compression cavity and a variable-capacity air inlet channel; a variable-volume piston; the variable-capacity sliding vane is movably arranged in the variable-capacity sliding vane groove, the variable-capacity air inlet channel is optionally communicated with the low-pressure environment or the high-pressure environment of the refrigeration system, when the variable-capacity air inlet channel is communicated with the low-pressure environment of the refrigeration system, the variable-capacity sliding vane is stopped to abut against the peripheral wall of the variable-capacity piston, and when the variable-capacity air inlet channel is communicated with the high-pressure environment of the refrigeration system, the variable-capacity sliding vane is separated from the variable-; and the pressure stabilizing channel is used for communicating the variable-capacity compression cavity with a high-pressure area of the rotary compressor when the variable-capacity air inlet channel is communicated with a high-pressure environment of the refrigerating system. According to the rotary compressor provided by the embodiment of the invention, the cylinder-removing operation is more stable, and the reliability is higher.

Description

Rotary compressor and refrigeration system with same

Technical Field

The invention relates to the field of compressors, in particular to a rotary compressor and a refrigerating system with the rotary compressor.

Background

With the depletion of global resources and the deterioration of the environment, energy efficiency and low cost are being pursued for air conditioners, refrigerators and the like. In order to deal with the problem, the capacity control technology of the variable capacity rotary compressor is continuously developed, so that the technical scheme for improving the capacity control of the refrigeration system is easier to apply and is more favorable in terms of reliability and cost. Among the correlation technique, inhale through the high-low pressure that draws pressure device to introduce refrigerating system pressure control varactor compression chamber and realize breaking away from or the normal operating of varactor cylinder, among the above-mentioned varactor mode, the varactor cylinder takes off the jar operation, when pressure on the refrigerating system who introduces is undulant along with refrigerating system load change, originally mutually break away from when the varactor cylinder takes off the jar operation gleitbretter and the piston have the possibility of laminating, and the varactor mode has the risk of losing efficacy promptly, exists and improves the space.

Disclosure of Invention

The present invention is directed to solving, at least to some extent, one of the technical problems in the related art. Therefore, the invention provides a rotary compressor with more stable cylinder releasing operation.

Another object of the present invention is to provide a refrigeration system having the above rotary compressor.

According to the rotary compressor of the embodiment of the first aspect of the present invention, the electric motor and the rotary compression mechanism section driven by the electric motor are housed in the sealed case, the compression mechanism section includes at least one set of variable-capacity cylinder assemblies, and the variable-capacity cylinder assemblies include: the variable-capacity air cylinder is provided with a variable-capacity slide groove, a variable-capacity compression cavity and a variable-capacity air inlet channel; the variable-capacity piston is eccentrically and rotatably arranged in the variable-capacity compression cavity; the variable-volume slide sheet is movably arranged in the variable-volume slide sheet groove, the variable-volume air inlet channel is optionally communicated with a low-pressure environment of a refrigeration system or a high-pressure environment of the refrigeration system, when the variable-volume air inlet channel is communicated with the low-pressure environment of the refrigeration system, the variable-volume slide sheet starts to stop abutting against the peripheral wall of the variable-volume piston, and when the variable-volume air inlet channel is communicated with the high-pressure environment of the refrigeration system, the variable-volume slide sheet is separated from the variable-volume piston; and the pressure stabilizing channel is used for communicating the variable volume compression cavity with a high-pressure area of the rotary compressor when the variable volume air inlet channel is communicated with a high-pressure environment of the refrigerating system.

According to the rotary compressor provided by the embodiment of the invention, the variable-capacity compression cavity and the high-pressure area of the rotary compressor are communicated when the variable-capacity air cylinder assembly is in cylinder releasing operation by arranging the pressure stabilizing channel, so that the fluctuation of pressure introduced into a refrigeration system is inhibited, the stop of the variable-capacity piston and the variable-capacity sliding vane is avoided, and the cylinder releasing operation is more stable.

In some embodiments of the present invention, the first port of the surge duct is connected to the variable displacement vane groove, the second port of the surge duct is connected to the high pressure region of the rotary compressor, the variable displacement vane has a first position and a second position, the first port of the surge duct is communicated with the variable displacement vane groove when the variable displacement vane is located at the first position, and the variable displacement vane blocks the first port of the surge duct from the variable displacement vane groove when the variable displacement vane is located at the second position.

In some embodiments of the present invention, the rotary compressor includes a main bearing and a secondary bearing, one of the main bearing and the secondary bearing sealing the variable-volume cylinder, the surge passage being provided on the one of the main bearing and the secondary bearing.

In some embodiments of the present invention, a discharge chamber is provided on the one of the main bearing and the secondary bearing, a portion of the one of the main bearing and the secondary bearing is opposite to the variable-capacity vane groove, a first port of the surge tank is provided on the portion of the main bearing or the secondary bearing, and a second port of the surge tank is communicated with the discharge chamber.

In some embodiments of the present invention, the rotary compressor includes a partition plate for sealing the variable-capacity cylinder, and the surge passage is provided on the partition plate.

In some embodiments of the present invention, a portion of the partition plate is opposite to the positive-displacement vane groove, a first port of the surge passage is provided on the portion of the partition plate, and a second port of the surge passage communicates with a high-pressure region in the housing.

In some embodiments of the invention, the equivalent diameter of the first port of the pressure stabilizing channel is d1, the width of the variable-volume slide groove is d2, and the minimum cross-section equivalent diameter of the pressure stabilizing channel is d3, wherein d1 is more than or equal to 1mm, d3 is more than or equal to 1mm, and d2 is more than or equal to d1+ 0.1.

In some embodiments of the invention, in the extending direction of the variable-capacity slide groove, the minimum distance between the first port of the pressure stabilizing channel and the inner wall of the variable-capacity cylinder is L1, wherein L1 is more than or equal to 2 mm.

In some embodiments of the present invention, the rotary compressor further comprises: and the variable-volume sliding vane limiting device is used for positioning the variable-volume sliding vane at a position separated from the variable-volume piston when the variable-volume compression cavity is communicated with a high-pressure area of the rotary compressor.

In some embodiments of the present invention, the variable-capacity sliding vane limiting device includes a magnet structure, and when the pressure stabilizing channel communicates the variable-capacity compression chamber with a high-pressure region of the rotary compressor, the variable-capacity sliding vane is positioned at one end of the variable-capacity sliding vane groove far away from the variable-capacity piston under the magnetic force of the magnet structure.

In some embodiments of the present invention, the rotary compressor includes a main bearing, a secondary bearing, and a partition plate, the variable-capacity cylinder is interposed between one of the main bearing and the secondary bearing and the partition plate, the magnet structure includes a first group of magnets and a second group of magnets, two groups of magnets are respectively disposed on the one of the main bearing and the secondary bearing and the partition plate, and a distance between the two groups of magnets and a center of an inner diameter of the variable-capacity cylinder is different in an extending direction of the variable-capacity vane groove.

In some embodiments of the present invention, in the extending direction of the varactor slide groove, the distance between the first port of the voltage stabilizing channel and the first set of magnets is L2, the distance between the first port of the voltage stabilizing channel and the second set of magnets is L3, wherein L3-L2 is less than or equal to 10mm, and L3-L2 is greater than 0.

In some embodiments of the invention, the length of the variable-capacity slide is L4, and the minimum distance between one end of the first group of magnets adjacent to the variable-capacity piston and the inner wall of the variable-capacity cylinder is L5, wherein L3 is not less than L4, and L5 is not less than L4.

In some embodiments of the present invention, the rotary compressor includes a main bearing, a secondary bearing and a partition plate, the variable-capacity cylinder is sandwiched between one of the main bearing and the secondary bearing and the partition plate, the magnet structure is disposed on the one of the main bearing and the secondary bearing, the pressure stabilizing channel is disposed on the partition plate, a distance between a first port of the pressure stabilizing channel and the magnet structure is L8, a length of the variable-capacity sliding piece is L4, and L8 is greater than or equal to L4.

In some embodiments of the present invention, the variable-volume sliding vane limiting device is an elastic member disposed at an end of the variable-volume sliding vane groove away from the variable-volume piston, one end of the elastic member is connected to the variable-volume sliding vane, the other end of the elastic member is connected to the variable-volume cylinder, and the other end of the elastic member is an end away from the variable-volume piston.

In some embodiments of the present invention, in the extending direction of the variable-capacity slide groove, the original length of the elastic member without tensile force is L6, the length of the variable-capacity slide is L4, and the minimum distance between the opening of the variable-capacity slide groove facing the variable-capacity piston and the connecting position of the variable-capacity cylinder and the other end of the elastic member is L7, wherein L7 is greater than or equal to L6+ L4.

In some embodiments of the present invention, the rotary compressor further includes a pressure guiding device, the pressure guiding device is connected to the refrigeration system, and the pressure guiding device selectively communicates a low-pressure environment of the refrigeration system with the variable-volume intake passage, or the pressure guiding device selectively communicates a high-pressure environment of the refrigeration system with the variable-volume intake passage.

A refrigeration system according to an embodiment of the second aspect of the present invention includes the rotary compressor of the first aspect.

The refrigeration system provided by the embodiment of the invention has the advantages of stable operation and high efficiency.

Drawings

Fig. 1 is a schematic view of a structure of a rotary compressor of the present invention;

fig. 2 is a longitudinal sectional view of a compression mechanism portion of the first embodiment of the rotary compressor of the present invention;

fig. 3 is an enlarged view at B of fig. 2;

fig. 4 is a sectional view taken along a-a of the end of the first embodiment of the rotary compressor of fig. 2 adjacent to the capacity-changing piston where the capacity-changing vane slides to the capacity-changing vane groove;

FIG. 5 is a sectional view taken along A-A in the cylinder deactivation state of the first embodiment of the rotary compressor of FIG. 2;

fig. 6 is a sectional view taken along a-a in a normal operation of the first embodiment of the rotary compressor of fig. 2;

fig. 7 is a longitudinal sectional view illustrating a normal operation of the second embodiment of the rotary compressor of the present invention;

FIG. 8 is a longitudinal sectional view of the second embodiment of the rotary compressor of the present invention at the time of de-cylinder;

fig. 9 is a transverse sectional view of the second embodiment of the rotary compressor of the present invention at the end of the variable-capacity vane sliding to the variable-capacity vane groove adjacent to the variable-capacity piston;

fig. 10 is a transverse sectional view of the second embodiment of the rotary compressor of the present invention at the time of de-cylinder;

fig. 11 is a transverse sectional view of a second embodiment of the rotary compressor of the present invention in normal operation;

fig. 12 is a longitudinal sectional view of a compression mechanism portion of a third embodiment of a rotary compressor of the present invention;

fig. 13 is an enlarged view at C of fig. 12;

FIG. 14 is a schematic view of the refrigeration system of the present invention in a cooling mode;

fig. 15 is a schematic view of the refrigeration system of the present invention in a heating mode.

Reference numerals:

the refrigeration system 1000, the rotary compressor 100, the electric motor 101, the compression mechanism portion 102, the housing 103, the variable-capacity cylinder 1, the variable-capacity slide groove 11, the variable-capacity compression cavity 12, the variable-capacity intake passage 13, the variable-capacity piston 2, the variable-capacity slide 3, the pressure stabilizing passage 4, the first port a1, the second port a2, the main bearing 51, the auxiliary bearing 52, the exhaust cavity 53, the partition plate 6, the variable-capacity slide limiting device 7, the first group of magnets 71, the second group of magnets 72, the elastic member 73, the pressure guide device 8, the cylinder 91, the slide 92, the piston 93, the crankshaft 94, the indoor heat exchanger 200, the outdoor heat exchanger 300, the throttle device 400, and the four-way valve 500.

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.

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.

Referring to fig. 1 to 13, a rotary compressor 100 according to an embodiment of the present invention is described in detail, the rotary compressor 100 is a variable capacity rotary compressor 100, and the rotary compressor 100 may be applied to a refrigeration system 1000 for compressing and driving a refrigerant in the refrigeration system 1000.

As shown in fig. 1 to 13, in a rotary compressor 100 according to an embodiment of the present invention, a sealed casing 103 houses therein an electric motor 101 composed of a stator and a rotor, and a compression mechanism section 102. The compression mechanism portion 102 includes at least one set of variable-capacity cylinder assemblies, and the variable-capacity cylinder assemblies include a variable-capacity cylinder 1, a variable-capacity piston 2, a variable-capacity sliding vane 3, and a pressure-stabilizing passage 4.

In some embodiments, as shown in fig. 1 to 13, the rotary compressor 100 may be a double-cylinder rotary compressor 100, and the compression mechanism part 102 of the double-cylinder rotary compressor 100 may further include a cylinder 91, a main bearing 51 and a sub bearing 52 located at both sides of the cylinder 91 and the variable capacity cylinder 1, and a partition plate 6 disposed between the cylinder 91 and the variable capacity cylinder 1.

Of course, in other embodiments, the rotary compressor 100 of the present invention may also be a multi-cylinder rotary compressor 100, and the compression mechanism portion 102 of the multi-cylinder rotary compressor 100 may also include a plurality of cylinders 91, and a main bearing 51 and a sub-bearing 52 located at both sides of the plurality of cylinders 91 and at least one variable-capacity cylinder 1 therein, and a plurality of partition plates 6 disposed between adjacent cylinders 91 and variable-capacity cylinders 1, between adjacent two cylinders 91, or between adjacent two variable-capacity cylinders 1.

As shown in fig. 4-6 and 9-11, the variable displacement cylinder 1 is provided with a variable displacement vane groove 11, a variable displacement compression chamber 12 and a variable displacement intake passage 13, the variable displacement piston 2 is eccentrically and rotatably provided in the variable displacement compression chamber 12, and the variable displacement vane 3 is movably provided in the variable displacement vane groove 11.

The variable-volume air inlet channel 13 of the variable-volume cylinder 1 is selectively communicated with the low-pressure environment of the refrigeration system 1000 or the high-pressure environment of the refrigeration system 1000, that is, the variable-volume air inlet channel 13 can be communicated with the low-pressure environment of the refrigeration system 1000, so that low-pressure gas can enter the variable-volume air inlet channel 13 from the refrigeration system 1000; the variable volume inlet passage 13 may also be in communication with the high pressure environment of the refrigeration system 1000 such that high pressure gas may enter the variable volume inlet passage 13 from the refrigeration system 1000.

The pressure stabilizing passage 4 is used for communicating the variable-volume compression chamber 12 with the high-pressure region of the rotary compressor 100 when the variable-volume intake passage 13 of the variable-volume cylinder 1 is communicated with the high-pressure environment of the refrigeration system 1000.

Alternatively, as shown in fig. 12 and 13, the high pressure region of the rotary compressor 100 may be a high pressure region within the casing 103 of the rotary compressor 100, and as shown in fig. 1, 2, 3, 7 and 8, the high pressure region of the rotary compressor 100 may be a high pressure region at another position of the rotary compressor 100, for example, the discharge chamber 53 provided on the sub-bearing 52.

As shown in fig. 6, 7 and 11, when the variable-capacity intake passage 13 communicates with the low-pressure environment of the refrigeration system 1000, one end of the variable-capacity sliding vane 3 facing the variable-capacity piston 2 is low pressure, and one end away from the variable-capacity piston 2 is high pressure in the housing 103, and under the action of the pressure difference, the variable-capacity sliding vane 3 starts to stop abutting against the outer peripheral wall of the variable-capacity piston 2, and the rotary compressor 100 is in a normal operation mode, so as to realize normal compression.

As shown in fig. 5, fig. 8 and fig. 10, when the variable-volume intake channel 13 is communicated with the high-pressure environment of the refrigeration system 1000, one end of the variable-volume sliding vane 3 facing the variable-volume piston 2 is high pressure, one end far away from the variable-volume piston 2 is high pressure in the housing 103, the pressure difference between the two ends of the variable-volume sliding vane 3 is small at this time, the variable-volume sliding vane 3 is separated from the variable-volume piston 2, the rotary compressor 100 is in a cylinder releasing mode, and the pressure stabilizing channel 4 is communicated with the high-pressure area of the variable-volume compression cavity 12 and the rotary compressor 100, so that the high-pressure fluctuation introduced into the variable-volume compression cavity 12 due to the change of the high-pressure environment working condition of the refrigeration system 1000 can be effectively suppressed, thereby effectively preventing the high-pressure gas introduced into the refrigeration system 1000, the situation that the.

In fig. 2 and 4 to 12, the high-pressure environment of the refrigeration system 1000 and the high-pressure region of the rotary compressor 100 are both denoted by Pd, and the low-pressure environment of the refrigeration system 1000 is denoted by Ps.

According to the rotary compressor 100 provided by the embodiment of the invention, the pressure stabilizing channel 4 is arranged, so that the variable-volume compression cavity 12 is communicated with the high-pressure area of the rotary compressor 100 during cylinder releasing operation, the influence of pressure fluctuation on the introduced refrigeration system 1000 along with the load change of the refrigeration system 1000 is effectively inhibited, the variable-volume piston 2 is prevented from being attached to the variable-volume sliding sheet 3 during cylinder releasing operation, and the stability during cylinder releasing operation is improved.

Optionally, the rotary compressor 100 may further include a pressure guiding device 8, the pressure guiding device 8 is connected to the refrigeration system 1000, the pressure guiding device 8 may selectively communicate the low-pressure environment of the refrigeration system 1000 with the variable-volume intake passage 13, or the pressure guiding device 8 may selectively communicate the high-pressure environment of the refrigeration system 1000 with the variable-volume intake passage 13, that is, the pressure guiding device 8 may switchably input the high-pressure gas or the low-pressure gas in the refrigeration system 1000 into the variable-volume intake passage 13, so that the rotary compressor 100 is switched between the normal operation mode and the cylinder deactivation mode. Optionally, the pressure inducing device 8 is a four-way valve 500.

The first, second and third embodiments of the rotary compressor 100 according to the present invention will be described in detail with reference to fig. 1 to 13.

The first embodiment:

referring to fig. 1 to 6, the rotary compressor 100 includes a housing 103, an electric motor 101 sealed in the housing 103, and a rotary compression mechanism 102, wherein the compression mechanism 102 includes a main bearing 51, a sub bearing 52, a crankshaft 94, a partition plate 6, a pressure guide device 8, a cylinder assembly, a variable capacity cylinder assembly, and a variable capacity vane position limiter 7.

As shown in fig. 2, the cylinder assembly includes a cylinder 91, a sliding vane 92, and a piston 93, the sliding vane 92 is movably disposed on the cylinder 91, the sliding vane 92 is capable of reciprocating and always abuts against an outer peripheral wall of the piston 93, the piston 93 is fixed on an eccentric portion of a crankshaft 94, and the piston 93 is eccentrically and rotatably disposed in a compression chamber of the cylinder 91.

As shown in fig. 4-6, the variable-capacity cylinder assembly includes a variable-capacity cylinder 1, a variable-capacity piston 2, a variable-capacity slide 3, and a pressure-stabilizing passage 4.

As shown in fig. 2, the diaphragm 6 is interposed between the cylinder 91 and the variable displacement cylinder 1, the cylinder 91 is interposed between the main bearing 51 and the diaphragm 6, and the variable displacement cylinder 1 is interposed between the diaphragm 6 and the sub-bearing 52.

Varactor gleitbretter stop device 7 is used for when varactor compression chamber 12 and rotary compressor 100's high pressure region intercommunication, with varactor gleitbretter 3 location in the position with varactor piston 2 separation to further promote, stability when taking off the jar operation. Optionally, the variable-capacitance sliding-vane limiting device 7 includes a magnet structure, and when the pressure stabilizing channel 4 communicates the variable-capacitance compression cavity 12 with the high-pressure region of the rotary compressor 100, the variable-capacitance sliding vane 3 is positioned at one end of the variable-capacitance sliding-vane groove 11, which is far away from the variable-capacitance piston 2, under the magnetic action of the magnet structure.

As shown in fig. 2, 3 and 5, the first port a1 of the surge tank 4 is connected to the variable displacement vane groove 11, the second port a2 of the surge tank 4 is connected to a high pressure region of the rotary compressor 100, and the variable displacement vane 3 has a first position and a second position, as shown in fig. 5, when the variable displacement vane 3 is located at the first position, the first port a1 of the surge tank 4 is communicated with the variable displacement vane groove 11, and when the variable displacement vane 3 is located at the second position, as shown in fig. 6, the variable displacement vane 3 blocks the first port a1 of the surge tank 4 from the variable displacement vane groove 11.

Specifically, as shown in fig. 5, the sub-bearing 52 seals the variable displacement cylinder 1, the surge passage 4 is provided on the sub-bearing 52, and the sub-bearing 52 is provided with the discharge chamber 53, in which case the discharge chamber 53 is a high pressure region of the rotary compressor 100, a portion of the sub-bearing 52 is opposed to the variable displacement vane groove 11, the first port a1 of the surge passage 4 is provided on the portion of the sub-bearing 52, and the second port a2 of the surge passage 4 is communicated with the discharge chamber 53. Accordingly, the conventional discharge chamber 53 is fully utilized, and the rotary compressor 100 is simple in structure and easy to manufacture.

As shown in FIG. 5, the equivalent diameter of the first port A1 of the surge tank 4 is d1, the width of the variable-capacity vane slot 11 is d2, and the minimum cross-sectional equivalent diameter of the surge tank 4 is d3 (not shown), wherein d1 is more than or equal to 1mm, d3 is more than or equal to 1mm, and d2 is more than or equal to d1+ 0.1.

As shown in FIG. 5, the minimum distance between the first port A1 of the surge tank 4 and the inner wall of the varactor cylinder 1 in the extending direction of the varactor vane groove 11 is L1, where L1 is 2mm or more.

As shown in fig. 2, the variable displacement cylinder 1 is interposed between the sub-bearing 52 and the diaphragm 6, the magnet structure includes a first group of magnets 71 and a second group of magnets 72, one of the two groups of magnets is disposed on the sub-bearing 52, the other of the two groups of magnets is disposed on the diaphragm 6, for example, the first group of magnets 71 is disposed on the sub-bearing 52, the second group of magnets 72 is disposed on the diaphragm 6, the two groups of magnets are spaced from the center of the inner diameter of the variable displacement cylinder 1 in the extending direction of the variable displacement vane groove 11, and the two groups of magnets are disposed so that the variable displacement vane 3 is more stably fixed at a position separated from the variable displacement piston 2, thereby increasing the stability during cylinder disengaging operation.

Specifically, as shown in fig. 4, in the extending direction of the variable-capacity vane slot 11, the distance between the first port a1 of the surge tank 4 and the first group of magnets 71 is L2, the distance between the first port a1 of the surge tank 4 and the second group of magnets 72 is L3, wherein L3-L2 is less than or equal to 10mm, and L3-L2 is greater than 0.

As shown in FIG. 4, the length of the variable-capacity slide plate 3 is L4, and the minimum distance between one end of the first group of magnets 71 adjacent to the variable-capacity piston 2 and the inner wall of the variable-capacity cylinder 1 is L5, wherein L3 is not less than L4, and L5 is not less than L4.

By defining the structural dimensions, such as d1, d2, d3, L1, L2, L3, L4 and L5, when the variable-capacity cylinder assembly operates, as shown in FIG. 6, the first port A1 of the pressure stabilizing channel 4 is shielded and sealed by the variable-capacity sliding vane 3; as shown in fig. 4, when the cylinder is released and the variable displacement piston 2 moves to the top, the variable displacement vane 3 is stopped being attracted by the first group of magnets 71 and further attracted by the second group of magnets 72; as shown in fig. 5, the first port a1 of the pressure stabilizing channel 4 is communicated with the variable-volume slide groove 11, so as to communicate the variable-volume compression cavity 12 with the exhaust cavity 53, suppress pressure fluctuation of the variable-volume compression cavity 12, play a role in stabilizing pressure, and effectively prevent the exhaust valve plate of the exhaust cavity 53 from being opened. It will be appreciated that the position of the varactor 3 shown in fig. 4 is an intermediate position running from the position in fig. 6 to the position in fig. 5.

The operation of the first embodiment of the rotary compressor 100 according to the present invention will be described in detail with reference to fig. 1 to 6:

as shown in fig. 4 and fig. 6, when the gas introduced into the variable volume inlet channel 13 of the variable volume cylinder 1 by the pressure introduction device 8 is low pressure, the variable volume inlet channel 13 is communicated with the low pressure environment of the refrigeration system 1000, one end of the variable volume sliding vane 3 facing the variable volume piston 2 is low pressure, one end away from the variable volume piston 2 is high pressure in the housing 103, under the action of the pressure difference, the variable volume sliding vane 3 starts to stop abutting against the peripheral wall of the variable volume piston 2, the rotary compressor 100 is in a normal operation mode to realize normal compression, at this time, the first port a1 of the pressure stabilizing channel 4 is shielded and sealed by the end face of the variable volume sliding vane 3, the pressure stabilizing channel 4 is isolated from the variable volume sliding vane groove 11, that is, the pressure stabilizing channel 4 is isolated from the variable volume compression cavity 12.

As shown in fig. 5, when the pressure guiding device 8 enters the variable volume intake passage 13 of the variable volume cylinder 1, the variable volume intake passage 13 is in communication with the high pressure environment of the refrigeration system 1000, the end of the variable volume slide 3 facing the variable volume piston 2 is high pressure, the end far away from the variable volume piston 2 is high pressure in the housing 103, the pressure difference between the two ends of the variable volume slide 3 is small, the variable volume slide 3 is positioned at the end far away from the variable volume piston 2 under the adsorption action of the second group of magnets 71 and the second group of magnets 72, the variable volume slide 3 is separated from the variable volume piston 2, the rotary compressor 100 is in the cylinder release mode, the first port a1 of the pressure stabilizing passage 4 is in communication with the variable volume slide groove 11, because the variable volume slide groove 11 is in communication with the variable volume compression chamber 12, and the second port a2 of the pressure stabilizing passage 4 is in communication with the exhaust chamber 53, so that the variable volume compression chamber 12 is in, the high pressure in the exhaust chamber 53 can be effectual to restrain and lead to introducing the high pressure fluctuation in the varactor compression chamber 12 because of the operating mode change of refrigerating system 1000 to lead to the condition of varactor gleitbretter 3 and varactor piston 2 laminating because of the pressure fluctuation when effectively preventing to introduce the high pressure.

Of course, depending on the location of the variable-displacement cylinder 1, in other embodiments, the variable-displacement cylinder 1 may be sealed by the main bearing 51, that is, in this embodiment, the variable-displacement cylinder 1 is sandwiched between the main bearing 51 and the partition plate 6, the surge channel 4 may be disposed on the main bearing 51, a portion of the main bearing 51 is opposite to the variable-displacement vane slot 11, the first port a1 of the surge channel 4 is disposed on the portion of the main bearing 51, the main bearing 51 may be provided with the exhaust cavity 53, the second port a2 of the surge channel 4 is communicated with the exhaust cavity 53, two sets of magnets of the variable-displacement vane limiting device 7 may be disposed on the main bearing 51 and the partition plate 6, respectively, for example, the first set of magnets 71 is disposed on the main bearing 51, and the second set of magnets 72 is disposed on the.

Second embodiment:

referring to fig. 7 to 11, the rotary compressor 100 includes a housing 103, an electric motor 101 sealed in the housing 103, and a rotary compression mechanism 102, wherein the compression mechanism 102 includes a main bearing 51, a sub bearing 52, a crankshaft 94, a partition plate 6, a pressure guide device 8, a cylinder assembly, a variable-capacity cylinder assembly including a variable-capacity cylinder 1, a variable-capacity piston 2, a variable-capacity vane 3, and a surge duct 4, and a variable-capacity vane limiting device 7.

The rotary compressor 100 of the second embodiment is different from the rotary compressor 100 of the first embodiment in that: the concrete structure of the variable capacitance sliding vane limiting device 7 is different. As shown in fig. 7-11, in the second embodiment, the variable-volume slide limiting device 7 is an elastic member 73 disposed at an end of the variable-volume slide groove 11 away from the variable-volume piston 2, one end of the elastic member 73 is connected to the variable-volume slide 3, the other end of the elastic member 73 is connected to the variable-volume cylinder 1, and the other end of the elastic member 73 is an end away from the variable-volume piston 2.

In the extending direction of the variable-capacity slide groove 11, the original length of the elastic piece 73 without tensile force is L6, the length of the variable-capacity slide 3 is L4, and the minimum distance between the opening of the variable-capacity slide groove 11 facing the variable-capacity piston 2 and the connecting position of the variable-capacity cylinder 1 and the other end of the elastic piece 73 is L7, wherein L7 is more than or equal to L6+ L4.

As shown in fig. 7 and 11, when the gas entering the variable volume intake passage 13 of the variable volume cylinder 1 from the pressure guiding device 8 is low pressure, the variable volume slide 3 always abuts against the variable volume piston 2 under the action of the pressure difference, the rotary compressor 100 is in the normal operation mode, and the elastic member 73 is stretched.

As shown in fig. 8 and 10, when the gas introduced into the variable volume intake passage 13 of the variable volume cylinder 1 by the pressure introduction device 8 is high pressure, the pressure difference between the two ends of the variable volume slide 3 is small, the elastic member 73 returns to the original length, the variable volume slide 3 is positioned at one end away from the variable volume piston 2 under the action of the elastic member 73, the variable volume slide 3 is separated from the variable volume piston 2, and the rotary compressor 100 is in the cylinder release mode.

In the second embodiment, d1, d2, d3, L1 and L4 are defined as in the first embodiment, and by the definition of d1, d2, d3, L1, L4, L6 and L7, it can be ensured that when the variable-capacity cylinder assembly operates, as shown in fig. 11, the first port a1 of the surge channel 4 is shielded and sealed by the variable-capacity vane 3, as shown in fig. 9, when the variable-capacity piston 2 operates to the top, the variable-capacity vane 3 moves to a position where the variable-capacity vane 3 is separated from the variable-capacity piston 2 under the action of the elastic member 73, as shown in fig. 10, the first port a1 of the surge channel 4 is communicated with the variable-capacity vane groove 11, so as to communicate the variable-capacity compression chamber 12 with the exhaust chamber 53, so as to suppress the pressure fluctuation of the variable-capacity compression chamber 12 and play a role in pressure regulation. It will be appreciated that the position of the varactor 3 shown in fig. 9 is an intermediate position running from the position in fig. 11 to the position in fig. 10.

Third embodiment:

referring to fig. 12, the rotary compressor 100 includes a housing 103, a motor 101 sealed in the housing 103, and a rotary compression mechanism 102, wherein the compression mechanism 102 includes a main bearing 51, a sub bearing 52, a crankshaft 94, a partition plate 6, a pressure guide device 8, a cylinder assembly, a variable-capacity cylinder assembly including a variable-capacity cylinder 1, a variable-capacity piston 2, a variable-capacity vane 3, and a surge duct 4, and a variable-capacity vane limiting device 7.

The rotary compressor 100 of the third embodiment is different from the rotary compressor 100 of the first embodiment in that: the specific structure of the variable-capacity slip sheet limiting device 7 is different, the setting position of the pressure stabilizing channel 4 is different, and the high-pressure area of the rotary compressor 100 communicated with the pressure stabilizing channel 4 is different.

As shown in fig. 12 and 13, the rotary compressor 100 includes a partition plate 6, the partition plate 6 being used to seal the variable-capacity cylinder 1, a surge tank 4 being provided on the partition plate 6, a portion of the partition plate 6 being opposed to the variable-capacity vane groove 11, a first port a1 of the surge tank 4 being provided on the portion of the partition plate 6, and a second port a2 of the surge tank 4 being communicated with a high-pressure region in the casing 103.

Specifically, the surge tank 4 may include a vertical channel, one end of which is the first port a1 of the surge tank 4, connected to the positive displacement vane groove 11, and the other end of which is connected to one end of a lateral channel, the other end of which is the second port a2 of the surge tank 4, communicating with a high pressure region inside the housing 103. The structure of the pressure stabilizing channel 4 is simple and the manufacture is easy.

As shown in fig. 12, the variable-capacitance slider limiting device 7 includes a magnet structure provided on the secondary bearing 52.

When the gas that pressure device 8 goes into varactor inlet channel 13 of varactor cylinder 1 is the low pressure, varactor gleitbretter 3 ends varactor piston 2 all the time under the effect of pressure differential, varactor gleitbretter 3 cuts off first port A1 and varactor compression chamber 12 of steady voltage passageway 4, and rotary compressor 100 is in normal operating mode.

When the gas that draws pressure device 8 to go into varactor inlet channel 13 of varactor cylinder 1 is the high pressure, the pressure differential at varactor gleitbretter 3's both ends is less, varactor gleitbretter 3 is positioned the one end of keeping away from varactor piston 2 under the effect of magnet structure, varactor gleitbretter 3 removes the position to the first port A1 and the varactor compression chamber 12 intercommunication of steady voltage passageway 4, make the high pressure intercommunication in varactor compression chamber 12 and the casing 103, thereby make the both ends of varactor gleitbretter 3 be the exhaust high pressure in the casing 103, steady voltage reliability is higher.

As shown in fig. 12, the distance between the first port a1 of the surge-stabilizing channel 4 and the magnet structure is L8, the length of the variable displacement vane 3 is L4, L8 is equal to or greater than L4, in the third embodiment, the definition of d1, d2, d3, L1 and L4 is the same as that of the first embodiment, and by the definition of d1, d2, d3, L1, L4 and L8, it can be ensured that the first port a1 of the surge-stabilizing channel 4 is shielded and sealed by the variable displacement vane 3 when the variable displacement cylinder assembly operates, so as to realize a normal operation mode; when taking off the jar operation, varactor gleitbretter 3 moves the position that varactor gleitbretter 3 and varactor piston 2 break away from under the effect of the magnetic force of magnet structure, the first port A1 and varactor gleitbretter groove 11 intercommunication of steady voltage passageway 4, and then with the regional intercommunication of the high pressure in varactor compression chamber 12 and the casing 103, restrain the pressure oscillation of varactor compression chamber 12, play the steady voltage effect, and because varactor gleitbretter 3's both ends are the exhaust high pressure in the casing 103, the steady voltage reliability is higher.

Of course, according to the different installation positions of the variable-capacity cylinder 1, in other embodiments, the variable-capacity cylinder 1 may be sealed by the main bearing 51, that is, in this embodiment, the variable-capacity cylinder 1 is clamped between the main bearing 51 and the partition plate 6, and the variable-capacity sliding vane limiting device 7 is installed on the main bearing 51.

Of course, the structure of the rotary compressor 100 of the present invention is not limited thereto, and in some implementations, the variable-capacity sliding vane limiting device 7 of the rotary compressor 100 may adopt the structure of two sets of magnets in the first embodiment, and the pressure stabilizing channel 4 may be disposed on the partition plate 6.

In short, according to the rotary compressor 100 of the embodiment of the present invention, the pressure stabilizing channel 4 is provided in the variable capacity rotary compressor 100, so that the variable capacity compression chamber 12 is communicated with the high pressure region of the rotary compressor 100 when the variable capacity cylinder assembly is in cylinder releasing operation, thereby suppressing the fluctuation of the pressure introduced into the refrigeration system 1000, avoiding the stop between the variable capacity piston 2 and the variable capacity sliding vane 3, and making the cylinder releasing operation more stable.

Briefly describing a refrigeration system 1000 according to an embodiment of the present invention, as shown in fig. 14 and 15, the refrigeration system 1000 according to an embodiment of the present invention includes the rotary compressor 100 in the above-described embodiment, and includes an indoor heat exchanger 200, an outdoor heat exchanger 300, a throttling means 400, and a four-way valve 500.

As shown in fig. 14 and 15, the variable capacity intake passage 13 of the variable capacity cylinder 1 is connected to a pipe between the four-way valve 500 and the outdoor heat exchanger 300, and the refrigeration system 1000 can be controlled to switch between the cooling mode and the heating mode by controlling the communication state of the four ports of the four-way valve 500.

As shown in fig. 14, when the refrigeration system 1000 is in the cooling mode, the variable capacity intake passage 13 of the variable capacity cylinder 1 is at a high pressure, and the variable capacity cylinder 1 is in the cylinder deactivation operation. As shown in fig. 15, when the refrigeration system 1000 is in the heating mode, the variable capacity intake passage 13 of the variable capacity cylinder 1 is at a low pressure, and the variable capacity cylinder 1 is in a normal operation state.

According to the refrigeration system 1000 of the embodiment of the invention, by arranging the rotary compressor 100, the system operation is more stable and the efficiency is high.

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 description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," 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 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 rotary compressor characterized by a sealed housing that houses therein an electric motor and a rotary compression mechanism section driven by the electric motor, the compression mechanism section including at least one set of variable-capacity cylinder assemblies, the variable-capacity cylinder assemblies comprising:

the variable-capacity air cylinder is provided with a variable-capacity slide groove, a variable-capacity compression cavity and a variable-capacity air inlet channel;

the variable-capacity piston is eccentrically and rotatably arranged in the variable-capacity compression cavity;

the variable-volume slide sheet is movably arranged in the variable-volume slide sheet groove, the variable-volume air inlet channel is optionally communicated with a low-pressure environment of a refrigeration system or a high-pressure environment of the refrigeration system, when the variable-volume air inlet channel is communicated with the low-pressure environment of the refrigeration system, the variable-volume slide sheet starts to stop abutting against the peripheral wall of the variable-volume piston, and when the variable-volume air inlet channel is communicated with the high-pressure environment of the refrigeration system, the variable-volume slide sheet is separated from the variable-volume piston;

the pressure stabilizing channel is used for communicating the variable-capacity compression cavity with a high-pressure area of the rotary compressor when the variable-capacity air inlet channel is communicated with a high-pressure environment of the refrigeration system; wherein

The first port of the pressure stabilizing channel is connected with the variable-volume slide groove, the second port of the pressure stabilizing channel is connected with a high-pressure area of the rotary compressor, the variable-volume slide is provided with a first position and a second position, when the variable-volume slide is located at the first position, the first port of the pressure stabilizing channel is communicated with the variable-volume slide groove, and when the variable-volume slide is located at the second position, the variable-volume slide cuts off the first port of the pressure stabilizing channel and the variable-volume slide groove.

2. The rotary compressor of claim 1, comprising a primary bearing and a secondary bearing, one of the primary bearing and the secondary bearing sealing the varactor cylinder, the surge channel being disposed on the one of the primary bearing and the secondary bearing.

3. The rotary compressor of claim 2, wherein the one of the main bearing and the secondary bearing is provided with a discharge chamber, a portion of the one of the main bearing and the secondary bearing is opposite to the variable-capacity vane groove, a first port of the surge passage is provided on the portion of the main bearing or the secondary bearing, and a second port of the surge passage is communicated with the discharge chamber.

4. The rotary compressor of claim 1, comprising a partition plate for sealing the variable-capacity cylinder, the surge passage being provided on the partition plate.

5. The rotary compressor of claim 4, wherein a portion of the diaphragm is opposite to the variable-capacity vane groove, a first port of the surge passage is provided on the portion of the diaphragm, and a second port of the surge passage communicates with a high-pressure region in the casing.

6. The rotary compressor of claim 3 or 5, wherein the equivalent diameter of the first port of the surge channel is d1, the width of the variable-capacity vane groove is d2, and the minimum sectional equivalent diameter of the surge channel is d3, wherein d1 is not less than 1mm, d3 is not less than 1mm, and d2 is not less than d1+ 0.1.

7. The rotary compressor of claim 6, wherein a minimum distance of the first port of the surge channel from the inner wall of the variable-capacity cylinder in the extending direction of the variable-capacity vane groove is L1, wherein L1 is 2mm or more.

8. The rotary compressor of claim 1, further comprising: and the variable-volume sliding vane limiting device is used for positioning the variable-volume sliding vane at a position separated from the variable-volume piston when the variable-volume compression cavity is communicated with a high-pressure area of the rotary compressor.

9. The rotary compressor of claim 8, wherein the variable-capacity sliding vane limiting device comprises a magnet structure, and when the pressure stabilizing channel communicates the variable-capacity compression chamber with a high-pressure area of the rotary compressor, the variable-capacity sliding vane is positioned at one end of the variable-capacity sliding vane groove far away from the variable-capacity piston under the magnetic force of the magnet structure.

10. The rotary compressor according to claim 9, wherein the rotary compressor includes a main bearing, a sub bearing, and a partition plate, the variable-capacity cylinder is interposed between one of the main bearing and the sub bearing and the partition plate, the magnet structure includes a first group of magnets and a second group of magnets, the two groups of magnets are respectively provided on the one of the main bearing and the sub bearing and the partition plate, and the two groups of magnets are different in distance from a center of an inner diameter of the variable-capacity cylinder in an extending direction of the variable-capacity vane groove.

11. The rotary compressor of claim 10, wherein the first port of the surge tank is spaced apart from the first set of magnets by a distance L2 and the first port of the surge tank is spaced apart from the second set of magnets by a distance L3, wherein L3-L2 is 10mm or less, and L3-L2 is > 0, in the extending direction of the variable capacity vane groove.

12. The rotary compressor of claim 11, wherein the variable-capacity slide has a length of L4, and a minimum distance between an end of the first set of magnets adjacent to the variable-capacity piston and an inner wall of the variable-capacity cylinder is L5, wherein L3 is equal to or greater than L4, and L5 is equal to or less than L4.

13. The rotary compressor of claim 9, wherein the rotary compressor comprises a main bearing, a secondary bearing and a partition plate, the variable-capacity cylinder is sandwiched between one of the main bearing and the secondary bearing and the partition plate, the magnet structure is disposed on the one of the main bearing and the secondary bearing, the surge channel is disposed on the partition plate, a distance between a first port of the surge channel and the magnet structure is L8, a length of the variable-capacity vane is L4, and L8 is greater than or equal to L4.

14. The rotary compressor of claim 8, wherein the variable-capacity sliding vane position limiting device is an elastic member disposed at an end of the variable-capacity sliding vane groove away from the variable-capacity piston, one end of the elastic member is connected to the variable-capacity sliding vane, the other end of the elastic member is connected to the variable-capacity cylinder, and the other end of the elastic member is an end away from the variable-capacity piston.

15. The rotary compressor of claim 14, wherein an original length of the elastic member free from a pulling force in an extending direction of the variable-capacity vane groove is L6, a length of the variable-capacity vane is L4, and a minimum distance between an opening of the variable-capacity vane groove toward the variable-capacity piston and a connection position of the variable-capacity cylinder and the other end of the elastic member is L7, wherein L7 is greater than or equal to L6+ L4.

16. The rotary compressor of claim 1, further comprising a pressure inducing device coupled to the refrigeration system, the pressure inducing device selectively communicating a low pressure environment of the refrigeration system with the variable-capacity intake passage, or the pressure inducing device selectively communicating a high pressure environment of the refrigeration system with the variable-capacity intake passage.

17. A refrigeration system comprising a rotary compressor as claimed in any one of claims 1 to 16.