CN110836183A

CN110836183A - Compressor and compression mechanism thereof

Info

Publication number: CN110836183A
Application number: CN201810941404.9A
Authority: CN
Inventors: 小津政雄; 王玲; 周杏标
Original assignee: Guangdong Meizhi Compressor Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd
Priority date: 2018-08-17
Filing date: 2018-08-17
Publication date: 2020-02-25

Abstract

The invention discloses a real compressor and a compression mechanism thereof, wherein the compression mechanism for the compressor comprises: cylinder, rolling piston and gleitbretter. The cylinder is provided with an air suction channel; the rolling piston is arranged in the cylinder; the gleitbretter with roll piston cooperation in order to form low-pressure chamber and high-pressure chamber in the cylinder, wherein, the passageway of breathing in includes main entrance and two at least reposition of redundant personnel passageways, two at least reposition of redundant personnel passageway all with the main entrance intercommunication extends towards opposite direction, the main entrance has the air inlet, two at least reposition of redundant personnel passageway all communicates same low-pressure chamber. According to the compression mechanism for the compressor of the embodiment of the invention, the backflow can be weakened.

Description

Compressor and compression mechanism thereof

Technical Field

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

Background

With the pursuit of people for comfortable life, the power consumption for refrigerating the air conditioner in summer and heating the air conditioner in winter is always larger, so that the efficient air conditioner is the pursuit of scientific research institutions and heating and ventilation air conditioning enterprises, the compressor is used as the heart of the air conditioner, and the improvement of the efficiency is the key for improving the efficiency of the air conditioner.

In the compressor, the backflow problem is obvious particularly in multi-stage compression, and the energy loss is caused by the operation efficiency of the compressor which is greatly influenced.

Disclosure of Invention

An object of the present invention is to provide a compression mechanism for a compressor, which can reduce a backflow.

Another object of the present invention is to provide a compressor.

The compression mechanism for a compressor according to an embodiment of the present invention includes: cylinder, rolling piston and gleitbretter. The cylinder is provided with an air suction channel; the rolling piston is arranged in the cylinder; the gleitbretter with roll piston cooperation in order to form low-pressure chamber and high-pressure chamber in the cylinder, wherein, the passageway of breathing in includes main entrance and two at least reposition of redundant personnel passageways, two at least reposition of redundant personnel passageway all with the main entrance intercommunication extends towards opposite direction, the main entrance has the air inlet, two at least reposition of redundant personnel passageway all communicates same low-pressure chamber.

According to the compression mechanism for the compressor of the embodiment of the invention, the backflow can be weakened.

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

in some embodiments, each of the flow dividing passages includes an inlet section and an outlet section in communication with each other, the inlet section communicating with the main passage, the outlet section communicating with the low pressure chamber, the outlet section increasing in radial dimension relative to the inlet section.

In some embodiments, an annular step structure is formed between the outlet peripheral edge of the inlet section and the inlet peripheral edge of the outlet section.

In some embodiments, the outlet of the outlet section communicates with the low pressure chamber along a tangential extension of the outlet section.

In some embodiments, the cylinder includes a cylinder body and an end cover, the cylinder body has a through hole extending in an up-down direction, the upper and lower ends of the cylinder body are closed by the end cover, the rolling piston is disposed in the through hole, and the suction channel is disposed on a wall of the cylinder body.

In some embodiments, the main passage of the suction passage extends in a direction perpendicular to an axis of the through hole, the suction passage includes two branch passages extending in an up-down direction, and two of the branch passages and the main passage of the suction passage are configured in a "T" shape penetrating an outer circumferential surface, an upper end surface, and a lower end surface of the cylinder.

In some embodiments, the cylinder includes a plurality of cylinder bodies arranged up and down, and an end cover is shared between two adjacent cylinder bodies.

In some embodiments, the outlet of the main passage is provided with a tapered hole which gradually decreases in the air intake direction.

In some embodiments, a groove is provided opposite the outlet of the main channel.

In some embodiments, the groove is gradually concave in a direction from the periphery to the center.

In some embodiments, the sliding pieces include at least two sliding pieces arranged at intervals in a direction surrounding the rolling piston, the two sliding pieces are respectively matched with the rolling piston to form a group of low-pressure cavities and high-pressure cavities, and the suction channel includes a plurality of low-pressure cavities in one-to-one correspondence.

The compressor according to the embodiment of the present invention includes: the compression mechanism is arranged in the shell and is a compression mechanism according to the above description; the motor is arranged in the shell and used for driving the rolling piston.

In some embodiments, a plurality of the compression mechanisms arranged in an axial direction of a drive shaft of the motor is provided in the housing.

Drawings

Fig. 1 is a longitudinal sectional view of a compression mechanism of a rotary compressor according to embodiment 1 of the present invention.

Fig. 2 shows a longitudinal sectional view of the low-pressure gas circuit in the cylinder in accordance with embodiment 1.

FIG. 3 shows a longitudinal cross-sectional view of the details of the low-pressure gas circuit and co-current gas in relation to embodiment 1.

Fig. 4 is a plan view of the compression chamber and the fluid member in relation to embodiment 1.

Fig. 5 is a plan view showing details of the high-pressure gas flow leaking into the low-pressure gas and the scroll groove in embodiment 1.

Fig. 6 shows a longitudinal section through the return gas flow in the low-pressure gas circuit in accordance with embodiment 1.

Fig. 7 is a longitudinal sectional view showing details of the low-pressure gas circuit and the counterflow gas in embodiment 1.

Fig. 8 is a longitudinal sectional view of the low-pressure gas circuit in embodiment 2 of the present invention.

Fig. 9 is a longitudinal sectional view of the low-pressure gas circuit in embodiment 2.

Fig. 10 is a plan view of the compression mechanism of the 1-cylinder compression chamber according to embodiment 3 of the present invention.

Fig. 11 shows a longitudinal sectional view of the cylinder according to embodiment 3.

Reference numerals: the motor 4, the compression mechanism 5, the rolling piston 14, the sliding vane 13, the groove 36c, the housing 2, the tapered hole 37, the low pressure chamber 11a, the high pressure chamber 11B, the crankshaft 8, the cylinder block 10, the compression chamber 11, the intake pipe 12, the (scroll type) fluid element 33A, the inlet and outlet groove 33A, the rotation groove 34a, the (scroll type) fluid element 33B, the inlet and outlet groove 33B, the rotation groove 34B, the cylindrical hole 36, the main bearing 40, and the sub bearing 45.

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 drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

Referring to fig. 1 to 11, a compression mechanism 5 for a compressor according to an embodiment of the present invention includes: cylinder, rolling piston 14 and sliding vane 13.

Specifically, the cylinder has an intake passage for introducing a fluid into the cylinder. A rolling piston 14 is provided in the cylinder. The sliding vane 13 and the rolling piston 14 cooperate to form a low pressure chamber 11a and a high pressure chamber 11b in the cylinder, the combination of the sliding vane 13 and the rolling piston 14 forms the low pressure chamber 11a and the high pressure chamber 11b, and after the fluid enters the low pressure chamber 11a, the fluid is pressurized and sent to the high pressure chamber 11b due to the rolling of the rolling piston 14.

The suction channel may include a main channel and at least two branch channels, wherein the main channel is a channel for communicating with an external component, and in the compressor, the main channel communicates with an inlet of the compressor. At least two reposition of redundant personnel passageways all communicate and extend towards opposite direction with the main entrance, and the main entrance has the air inlet, and at least two reposition of redundant personnel passageways all communicate same low pressure chamber 11 a.

According to the compression mechanism 5 for a compressor of the embodiment of the present invention, the backflow can be reduced. When the backflow occurs, the fluid flows to the main channel from the flow dividing channel, the flow dividing channel comprises a plurality of flow dividing channels, and the flow dividing channels are finally converged in the main channel, at the moment, the kinetic energy of the fluid flowing back from the flow dividing channels can be mutually offset, so that the strength of the decreased backflow is further reduced, and in addition, the backflow is further reduced under the suction effect of the compressor, so that the problem of reducing or even removing the backflow of the fluid is solved.

In some embodiments, to further attenuate backflow, each flow-splitting channel comprises an inlet section communicating with the main channel and an outlet section communicating with the low-pressure chamber 11a, the outlet section having an increased radial dimension with respect to the inlet section.

Among other things, in the following embodiments of the present invention, the outlet section is described as a rotating trough for convenience of description, because if backflow occurs, the backflow fluid will swirl around in the outlet section, thereby attenuating the energy of the backflow fluid. In addition, the outlet of the outlet section may be described as an inlet and outlet trough in the following embodiments, that is, the rotary trough described below in the present invention is the outlet section, and the outlet trough described below is the outlet of the outlet section.

In some embodiments, the inlet section is located in a central position of the outlet section in projection in a direction from the inlet section to the outlet section. During the occurrence of backflow, the backflow fluid will form a vortex in the outlet section, further reducing the backflow.

In other words, an annular step structure is formed between the outlet peripheral edge of the inlet section and the inlet peripheral edge of the outlet section, or a junction of the inlet section and the outlet section is formed into an annular step structure, that is, a gap is formed between each of the outlet peripheral edge of the inlet section and the inlet peripheral edge of the outlet section.

In some embodiments, the outlet of the outlet section communicates with the low pressure chamber 11a in a tangential extension of the outlet section.

In some embodiments, the cylinder includes a cylinder body 10 and end caps, the cylinder body 10 has a through hole extending in an up-down direction, the upper and lower ends of the cylinder body 10 are closed by the end caps, a rolling piston 14 is disposed in the through hole, and an air suction passage is disposed on a wall of the cylinder body 10.

In fact, the end caps of the present invention are a general term, and the main bearing and the secondary bearing described below are all considered as the end caps.

In some embodiments, the main passage of the suction passage extends in a direction perpendicular to the axis of the through-hole, the suction passage includes two branch passages extending in the up-down direction, and the two branch passages and the main passage of the suction passage are configured in a "T" shape penetrating the outer circumferential surface, the upper end surface, and the lower end surface of the cylinder 10.

Referring to fig. 7, the cylindrical hole 36 is formed by two flow dividing channels, wherein two sections of the cylindrical hole 36 above and below the tapered hole 3737 are respectively one flow dividing channel.

In some embodiments, the cylinder includes a plurality of cylinder bodies 10 arranged up and down, and an end cover is shared between two adjacent cylinder bodies 10.

In some embodiments, the outlet of the main passage is provided with a tapered bore 37 that tapers in the direction of the inlet air.

In some embodiments, a groove 36c is provided opposite the outlet of the main channel. When entering from the main channel, the fluid will be led to the groove 36c, and under the guiding action of the groove 36c, the fluid will be dispersed to enter the branch channel.

In some embodiments, the groove 36c is gradually concave in a direction from the periphery to the center.

In some embodiments, the sliding vane 13 includes at least two sliding vanes 13 arranged at intervals in a direction surrounding the rolling piston 14, and the two sliding vanes 13 respectively cooperate with the rolling piston 14 to form a set of low pressure chamber 11a and high pressure chamber 11b, and the suction passage includes a plurality of low pressure chambers 11a in one-to-one correspondence.

The compressor according to the embodiment of the present invention includes: the compressor comprises a shell 2, a compression mechanism 5 and a motor 4, wherein the compression mechanism 5 is arranged in the shell 2, and the compression mechanism 5 is the compression mechanism 5; the motor 4 is disposed in the housing 2, the motor 4 is connected to the rolling piston 14, specifically, the rolling piston 14 of the compression mechanism 5 is connected to a crankshaft, the motor 4 is connected to the crankshaft, and the power of the motor 4 is transmitted to the rolling piston 14 through the crankshaft.

In some embodiments, a plurality of compression mechanisms 5 arranged in the axial direction of the drive shaft of the motor 4 are provided in the housing 2.

Some specific embodiments of the present invention are described below with reference to the accompanying drawings.

In the compressor of the invention, a motor and a compression mechanism driven by the motor are arranged in a sealed shell; a cylinder-shaped compression chamber provided in a cylinder of the compression mechanism is connected to an intake passage; a rotary compressor is provided with a fluid control element which increases the gas resistance to the gas flowing from the intake passage to the compression chamber and the gas resistance to the gas flowing from the compression chamber to the intake passage.

The fluid control element includes a scroll-type fluid element including rotary grooves having holes formed in both side surfaces of the cylinder, an outlet groove having holes formed in the rotary grooves and the compression chamber, and a branch passage having a hole formed from the intake passage to the center of the rotary groove.

The outlet groove is disposed at a position adjacent to a vane provided in the cylinder.

In the compression mechanism, the scroll-type fluid element is provided to each of the element parts connected to the both side surfaces of the cylinder.

The element component is either a bearing slidably engaged with a crankshaft of the compression mechanism or an intermediate plate connected to a flat surface of the cylinder.

The scroll type fluid element is provided in each of the suction passages of two compression chambers defined by a rolling piston and 2 vane sections in a cylinder chamber formed by the cylinder.

The branch passage is formed with a tapered hole having a reduced inner diameter at an outlet of the suction passage, the tapered hole being formed at a center of the branch passage.

The compression mechanism is provided with at least two cylinders.

The re-expansion of the gas refrigerant leaking from the high pressure chamber 11b to the low pressure chamber 11a causes the low pressure gas to flow back from the low pressure chamber 11a to the suction pipe 12, thereby reducing the cooling capacity. Thus, a solution is mentioned in the present application which can reduce backflow.

The compressor includes cylindrical holes 36 branched from the intake pipe 12 to both side planes of the cylinder, and a scroll-type fluid element 33A and a scroll-type fluid element 33B opening into the compression chamber 11 at the outlet of the cylindrical holes. Due to the backflow prevention effect of the two fluid members, the backflow low pressure gas generated from the inlet and

outlet grooves

33a and 33b connected to the low pressure chamber 11a is greatly reduced.

The present invention relates to an improvement in a loss of refrigeration capacity caused by re-expansion of high-pressure gas leaking to a low-pressure side of a compression chamber by a backflow prevention effect of a fluid control element (fluid element) provided in a low-pressure gas passage formed in a cylinder compression chamber of a rotary compressor. The measure is to equip a fluid element with a 2-pole structure on a low-pressure gas channel.

In order to overcome the drawbacks of the related art, an additional suction valve is added to the outlet of the suction hole in the united states from 1968 to 1983. On the other hand, in recent experiments, it has been reported that the refrigerating capacity is improved by about 4% by adding a suction valve.

However, the suction valve of the rotary compressor has not been put to practical use for two reasons: (1) noise is increased due to the reciprocating motion of the air suction valve; (2) the reliability problem of the suction valve breakage occurs due to the long-term operation and the absorption of the liquid refrigerant.

The present invention is characterized in that, in order to improve the weakness of the above-described rotary compressor, a suction valve is not used, but a fluid control (Fluidics System) is introduced by applying 2 fluid elements (Fluidics).

In the present invention:

1. the freezing capacity can be improved by about 4% by providing a fluid control on the aspiration circuit.

2. Because the fluid control uses a fluid element without moving parts, there is no reliability problem. And the noise deterioration problem is not generated.

3. The selected fluid element is easy to process, and can be additionally processed on the existing part. Moreover, the additional cost is low.

4. The present invention can be widely applied to a multi-cylinder rotary compressor, a multi-stage rotary compressor, a capacity-controlled rotary compressor, a CO2 rotary compressor, and the like.

Some specific embodiments of the present invention are described below with reference to the drawings.

Implementation state 1:

the cylinder rotary compressor 1 shown in fig. 1 shows a motor 4 and a compression mechanism 5 fixed to the inner periphery of a hermetic casing 2. The lubricant oil sealed in the bottom of the casing 2 is not shown.

The compression mechanism 5 includes a cylinder having a cylindrical compression chamber 11 welded to the inner periphery of the casing 2, a main bearing 40 and a sub bearing 45 in contact with the upper and lower planes thereof, a crankshaft 8 slidably fitted to these bearings, a rolling piston 14 that revolves around the inner periphery of the compression chamber 11 driven by an eccentric shaft 8a, a vane 13 that reciprocates in contact with the rolling piston 14, and a vane spring 13a that presses the vane 13. The main bearing 40 has a discharge hole 41 and a discharge valve 41a, and the discharge muffler 44 discharging high-pressure gas has a muffler discharge hole 44 a.

Fig. 2 shows a gas refrigerant suction passage connecting the cylinder and the low pressure chamber 11a of the compression chamber 11. Fig. 3 is a detailed view of the suction passage described above, showing the suction gas flow. Fig. 4 is a plan view showing an x-section of fig. 2.

In fig. 2 and 3, the low-pressure gas flowing into the intake pipe 12 connected to the middle of the side surface of the cylinder from the accumulator 48 is divided equally in the upper and lower directions of the cylindrical hole 36 by the rolling piston revolving by the rotation of the crankshaft 8, flows into the rotary groove 34a from the cylindrical hole end 36a, flows into the rotary groove 34b from the cylindrical hole end 36b, and flows equally into the low-pressure chamber 11a from the inlet and outlet groove 33a and the inlet and outlet groove 33 b.

In fig. 3, a groove 36c (which may be referred to as a disk-shaped groove) formed at the tip of the suction pipe 12 reduces the resistance loss of the high-speed gas discharged from the tapered hole 37, and ensures that the gas is not erroneously branched into the cylindrical hole end 36a and the cylindrical hole end 36 b. The tapered hole 37 formed at the front end of the suction pipe 12 is a simple fluid element for reducing the flow rate of the low-pressure gas flowing back from the low-pressure chamber 11 a.

In fig. 4, the low-pressure gas flowing from the intake pipe 12 to the low-pressure chamber 11a is compressed by the rolling piston 14 revolving clockwise, becomes high-pressure gas, and is discharged from the exhaust hole 41 to the exhaust muffler 44. And then flows into the case 2 through the muffler discharge hole 44a (fig. 2). Therefore, the pressure of the housing 2, the pressure of the inner diameter of the rolling piston 14, and the like are high pressures.

The upper right drawing of fig. 4 is an enlarged plan view of a scroll-type fluid element (Vortex Diode) having a backflow prevention function, and shows a rotation groove 34B constituting the scroll-type fluid element 33B and a cylindrical hole end 36B opened at the center thereof. The width (W) of the side surface of the inlet/outlet groove 33b adjacent to the side surface of the slide 13 is about half of that of a conventional circular low-pressure gas hole.

In embodiment 1, since the inlet/outlet groove 33a and the outlet/inlet groove 33b are provided on both sides of the cylinder, the total opening area is not changed from the conventional one. The above is a stroke in which the low-pressure gas flow flows from the suction pipe 12 into the low-pressure chamber 11 a. In the following text, the scroll-type fluid element is referred to as a fluid element.

Fig. 5 shows the flow of high-pressure gas leaking into the low-pressure chamber during the operation of the rotary compressor, and the necessity of the fluid element, which is a characteristic of embodiment 1, will be described. Symbol a denotes high-pressure gas that leaks from a gap between the outer periphery of rolling piston 14 and the inner periphery of the cylinder. The symbol B indicates high-pressure gas that leaks from the inner diameter of the rolling piston 14 at high pressure through the upper and lower sliding surfaces thereof. Symbol C denotes high-pressure gas that leaks from the line contact surface between the tip of the vane 13 and the outer periphery of the rolling piston 14.

On the other hand, high-pressure gas leaks from the clearance between the main bearing 40 and the sub bearing 45 connected to the side sliding surface of the vane 13 and the side flat surfaces of the cylinder. The amount of these leakage gases is proportional to the pressure difference between the high pressure gas (Pd) and the low pressure gas (Ps), and the amount of re-expansion gas expanded into the low pressure gas in the low pressure chamber 11a becomes larger in proportion to the compression ratio of the high pressure gas (Pd) and the low pressure gas (Ps).

For example, when the refrigerant R410A used in air conditioning has a high-low pressure difference of 3MPa and a compression ratio of 3.0, the high-low pressure difference of CO2 used in a water heater is 7MPa, and the amount of leakage of high-pressure gas of CO2 is large compared with the case where the compression ratio is 3.3 times, and the re-expansion loss CO2 is increased by about 10%. The re-expansion loss reduces the amount of the suction gas in the low pressure chamber 11a, and the low pressure gas temperature greatly increases, so that the coefficient of performance (COP) of the compressor is reduced due to the loss of the refrigeration capacity of the compressor.

In addition, if the rotation number of the motor 4 is 60rps, 60 times of downstream and return flows of the low-pressure gas alternately occur within 1 second, and the flow rate is also large. The back flow reduces the amount of low pressure gas generated from suction line 12, resulting in a loss of compressor cooling capacity. In embodiment 1, as a means for preventing the backflow, the

fluid elements

33A and 33B are disposed on the upper and lower planes of the cylinder.

In fig. 5, the low-pressure gas having the increased pressure and temperature flows back to the inlet and

outlet grooves

33B and 33A formed on both sides of the cylinder and flows into the

fluid elements

33B and 33A by re-expansion of the high-pressure gas leaking from the low-pressure chamber 11 a. At this time, since the returned low-pressure gas rotates at a high speed along the inner circumference of the rotating groove 34b, the amount of gas that can flow from the cylindrical hole end 36a opened at the center to the cylindrical hole 36 is extremely small due to the effect of the centrifugal force.

Fig. 6 shows the low-pressure gas flow returning from the low-pressure chamber 11a to the suction pipe 12. Fig. 7 is a detailed view thereof. A portion (about 10%) of the low-pressure gas flowing back to the

fluid elements

33A and 33B from the low-pressure chamber 11a flows into the cylinder bore 36 from the opposite cylinder bore end 36a and 36B. Because the same amount of the scavenged gas impinges against one another in the cylindrical bore 36, the velocity of the scavenged gas is greatly reduced.

Therefore, the amount of low-pressure gas that can be returned to the intake pipe 12 from the opening end of the intake pipe 12 is only a small amount (about 4%), and a fluid control element having a function of preventing the return flow is established. The cylindrical hole 36 serves as a counter fluid element having the backflow prevention function of the 2 nd embodiment.

That is, the scroll type fluid element which is the fluid element of the 1 st fluid element and the opposed fluid element which is the fluid element of the 2 nd fluid element exert the function of preventing the back flow similarly to the suction valve provided in the reciprocating piston compressor. Further, in embodiment 1, the intake pipe 12 is connected to the outer peripheral side surface of the cylinder, but if it is connected to the side surface of the main bearing 40, the sub bearing 45, or the like, it does not hinder the intake pipe even if it is routed to the cylindrical hole 36 of the cylinder.

Implementation state 2:

embodiment 2 relates to the arrangement and capacity expansion of the

fluid elements

33A and 33B. As shown in fig. 8, in a design in which the thickness of 1 cylinder is small, such as a 1-cylinder rotary compressor or a multi-cylinder rotary compressor, the fluid elements may be disposed on the main bearing 40 and the sub-bearing 45.

Fig. 9 shows a means for reducing the gas resistance of the downstream flow by expanding the volumes of the

fluid elements

33A and 33B and further expanding the low-pressure flow path from the gas suction pipe 12 to the low-pressure chamber 11 a. Since the

fluid elements

33A and 33B respectively added to the main bearing 40 and the sub bearing 45 are connected to the rotation grooves 34a and 34B provided in the cylinder, respectively, the volumes of the

fluid elements

33A and 33B and the opening areas of the inlet and

outlet grooves

33A and 33B are enlarged by about 2 times.

On the other hand, if the inner diameters of the cylindrical hole 30 and the suction pipe 12 are enlarged, the low-pressure gas flow path is enlarged, and it is possible to apply the present invention to a rotary compressor mounted with a high-speed operation inverter motor such as 120 rps. In embodiment 2, the ends of the inlet and

outlet grooves

33a and 33b cannot be opened to the inner diameter of the rolling piston 14. In the multi-cylinder rotary compressor, since the intermediate plate is provided between 2 cylinders, the fluid element 33A and the fluid element 33B are provided on the intermediate plate in one or both of the main bearing 40 and the sub bearing 45.

Implementation state 3:

fig. 10 is a plan view of a compression mechanism 6 of the rotary compressor of 1 cylinder 2 compression chamber, and fig. 11 is an x sectional view of fig. 10. In fig. 10, 1 cylinder chamber 21 provided at the center of a cylinder 20 is divided into an a compression chamber 21a and a B compression chamber 21B having equal displacement volumes by one rolling piston 14 revolving clockwise and the opposed a vane 23 and B vane 24.

As in embodiment 1, the a suction pipe 22a and the B suction pipe 22B are connected to the fluid element 33A and the fluid element 33B having the backflow prevention function adjacent to the side surfaces of the a vane 23 and the B vane 24, respectively. Further, the exhaust hole 43a and the exhaust hole 43B opened in the main bearing 40 are opened in the a compression chamber 21a and the B compression chamber 21B, respectively.

The low-pressure gas intake circuit of embodiment 3 is the same design as embodiment 1. However, since the total of the displacement volumes of 2 compression chambers described above is almost equal to that in embodiment 1, the internal volume of the low-pressure gas intake circuit is designed to be smaller than that in embodiment 1.

By 1 rotation of the rolling piston 14, then low-pressure gas suction, compression and discharge in the a compression chamber 21a, low-pressure gas suction, compression and discharge also occur in the B compression chamber 21B. The backflow preventing effect of the expanded low-pressure gas leaking to the low-pressure chambers of the respective compression chambers through the

fluid elements

33B and 33A and the cylindrical holes 36 as in embodiment 1 improves the problem of the low refrigerating capacity. Further, the opening width W of the inlet and

outlet grooves

33a and 33b is shorter than that of the conventional suction port, and therefore, the cooling capacity is further improved.

As described in embodiments 1, 2, and 3, the fluid element is disposed in the intake circuit, and the re-expansion of the high-pressure gas leaking into the low-pressure chamber improves the cooling capacity, which is a common technique for the entire rotary compressor. For example, the present invention can be widely applied to a multi-cylinder compressor, a multi-stage compressor, a low-pressure compressor, a low-temperature refrigerator, a CO2 compressor, and the like, in which the compression method is a rotary type.

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; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

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

In the 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 compression mechanism for a compressor, comprising:

the air cylinder is provided with an air suction channel;

the rolling piston is arranged in the cylinder;

a sliding vane cooperating with the rolling piston to form a low pressure chamber and a high pressure chamber within the cylinder,

wherein, the suction channel includes main entrance and two at least reposition of redundant personnel passageways, at least two reposition of redundant personnel passageways all with the main entrance intercommunication extends towards opposite direction, the main entrance has the air inlet, at least two reposition of redundant personnel passageways all communicate same low pressure chamber.

2. The compression mechanism for a compressor as set forth in claim 1, wherein each of said diverging passages includes an inlet section and an outlet section in communication with each other, said inlet section communicating with said main passage, said outlet section communicating with said low pressure chamber, said outlet section increasing in radial dimension relative to said inlet section.

3. The compression mechanism for a compressor according to claim 2, wherein an annular step structure is formed between an outlet peripheral edge of the inlet section and an inlet peripheral edge of the outlet section.

4. The compression mechanism for a compressor as set forth in claim 3, wherein said outlet of said outlet section communicates with said low pressure chamber extending tangentially of said outlet section.

5. The compressing mechanism for compressor as set forth in any one of claims 1 to 4, wherein the cylinder includes a cylinder body having a through hole extending in an up-down direction therein and end caps closing both upper and lower ends thereof, the rolling piston being provided in the through hole, and the suction passage being provided on a wall of the cylinder body.

6. The compression mechanism for a compressor according to claim 5, wherein the main passage of the suction passage extends in a direction perpendicular to an axis of the through hole, the suction passage includes two of the branch passages extending in an up-down direction, and two of the branch passages and the main passage of the suction passage are configured in a "T" shape penetrating an outer circumferential surface, an upper end surface, and a lower end surface of the cylinder block.

7. The compressing mechanism for compressor as set forth in claim 5, wherein the cylinder includes a plurality of cylinder bodies arranged one above another, and one end cover is shared between two adjacent cylinder bodies.

8. The compression mechanism for a compressor according to any one of claims 1 to 4, wherein a tapered hole which is gradually reduced in an intake direction is provided at an outlet of the main passage.

9. The compression mechanism for a compressor according to any one of claims 1 to 4, wherein a groove is provided at a position opposite to an outlet of the main passage.

10. The compression mechanism for a compressor according to claim 9, wherein the groove is gradually recessed in a direction from a peripheral edge to a center.

11. The compressing mechanism for compressor as claimed in claim 1, wherein the sliding vane includes at least two spaced in a direction surrounding the rolling piston, and the two sliding vanes cooperate with the rolling piston to form a set of low pressure chamber and high pressure chamber, respectively, and the suction passage includes a plurality of one-to-one correspondence to the low pressure chambers.

12. A compressor, comprising:

a housing;

a compression mechanism disposed within the housing, the compression mechanism being in accordance with any one of claims 1-11;

the motor is arranged in the shell and used for driving the rolling piston.

13. The compressor according to claim 12, wherein a plurality of the compression mechanisms are provided in the housing, arranged in an axial direction of a drive shaft of the motor.