CN112524031B

CN112524031B - Flange structure, pump body assembly and fluid machine

Info

Publication number: CN112524031B
Application number: CN202011590383.4A
Authority: CN
Inventors: 徐嘉; 任丽萍; 杜忠诚; 李直; 张培林; 张荣婷
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2020-12-29
Filing date: 2020-12-29
Publication date: 2022-05-27
Anticipated expiration: 2040-12-29
Also published as: CN112524031A

Abstract

The invention provides a flange structure, a pump body assembly and a fluid machine. One side of the flange structure, which faces the cylinder sleeve, is provided with a silencing groove, the silencing groove extends along the circumferential direction of the flange structure, and the flange structure also comprises a flange exhaust hole which is communicated with the silencing groove; the outer peripheral face of the flange structure is provided with a plurality of connecting bosses extending out along the radial direction of the flange structure, and the plurality of connecting bosses are arranged along the circumferential interval of the flange structure so as to form a clearance concave part between two adjacent connecting bosses. The flange structure provided by the invention can solve the problems that the flange structure does not have a silencing function and is easy to generate vibration noise in the operation process of the conventional rotary cylinder compressor.

Description

Flange structure, pump body assembly and fluid machine

Technical Field

The invention relates to the related technical field of rotary cylinder compressors, in particular to a flange structure, a pump body assembly and a fluid machine.

Background

Use the revolving cylinder compressor as an example, the pump body subassembly of present compressor is for reaching the effect of noise reduction, and the outside that will go up the flange sets up extra muffler usually, goes up the flange and only provides the exhaust hole, guarantees that the gas in the cylinder can be smooth outwards flow through last flange to carry out the amortization in the muffler.

The pump body assembly of structure like this, the structure is comparatively complicated, and goes up the effect singleness of flange, can't realize the function of amortization.

Meanwhile, the flange structure is installed in a cantilever supporting mode, vibration noise is easy to generate, the noise reduction effect is unstable, and noise reduction is not facilitated.

Therefore, the existing rotary cylinder compressor has the problems that the flange structure does not have a silencing function and vibration noise is easy to generate in the operation process.

Disclosure of Invention

The invention mainly aims to provide a flange structure, a pump body assembly and a fluid machine, and aims to solve the problems that in the prior art, a rotary cylinder compressor does not have a noise reduction function and is easy to generate vibration noise.

In order to achieve the above object, according to one aspect of the present invention, there is provided a flange structure, wherein a noise reduction groove is formed in a side of the flange structure facing a cylinder liner, the noise reduction groove extends along a circumferential direction of the flange structure, the flange structure further includes a flange exhaust hole, and the flange exhaust hole is communicated with the noise reduction groove; the outer peripheral face of the flange structure is provided with a plurality of connecting bosses extending out along the radial direction of the flange structure, and the plurality of connecting bosses are arranged along the circumferential interval of the flange structure so as to form a clearance concave part between two adjacent connecting bosses.

Further, the silencing grooves are communicated end to end.

Further, the ends of the silencing grooves are not communicated, so that a blocking structure is formed between the ends of the silencing grooves.

Further, the distance between two adjacent connecting bosses is equal.

Further, in the axial direction of the flange structure, the connection bosses extend to both ends of the outer peripheral surface of the flange structure.

Furthermore, each connecting boss is provided with at least one welding spot.

Furthermore, the lateral wall of amortization recess has the rib structure of the center pin salient to the flange structure, and the rib structure is a plurality of, and a plurality of rib structures set up along the lateral wall interval of amortization recess to make the amortization recess have the width that sets up in turn and flow through regional and the narrow region that flows through.

Further, the number of the rib-shaped structures is more than 3 and less than 5.

Furthermore, the flange structure is provided with a flange hole, the flange hole and the central shaft of the flange structure are eccentrically arranged, the middle part of the flange structure is provided with a shaft neck, the shaft neck is formed by a part provided with a silencing groove, the flange hole penetrates through the axial end face of the shaft neck, and the peripheral circle of the shaft neck is coaxial with the peripheral circle of the flange structure.

Further, the side of the journal departing from the cylinder sleeve is provided with a convex ring structure protruding out of the end face of the flange structure, so that the total height H in the axial direction of the flange structure is larger than the height H1 between the two end faces in the axial direction of the flange structure, and the height H2 of the noise reduction groove in the axial direction of the flange structure is smaller than the height H1 between the two end faces in the axial direction of the flange structure.

Further, 0.5H < H1< 0.9H; and/or 0.3H < H2< 0.7H.

Further, 0.65H < H1< 0.75H; and/or 0.4H < H2< 0.6H.

Further, the side wall thickness L1 of the flange structure and the end face thickness L2 of the flange structure satisfy the following relationship: 0.05H < L1< 0.25H; 0.1H < L2< 0.4H.

Further, the side wall of the sound-deadening groove has a rib structure protruding toward the center axis of the flange structure, and the relationship between the minimum thickness L3 of the axial end face of the journal and the distance R3 between the rib structure and the center k2 of the journal is 0.05H < L3< R3.

Further, the middle part of the flange structure is provided with a shaft neck, an eccentric amount e is arranged between a center k2 of the shaft neck and a center k1 of a flange shaft hole of the flange structure, the distance between a center k1 of the flange shaft hole of the flange structure and an outer side groove wall of the sound attenuation groove is R1, the distance between the rib-shaped structure and a center k2 of the shaft neck is R3, the distance from the center k2 of the shaft neck to an inner side groove wall of the sound attenuation groove is R2, and the following relations are satisfied among R1, R2 and R3: 0.1< (R1-R2)/(R3-R2) < 0.4.

Further, 0.15< (R1-R2)/(R3-R2) < 0.25.

Further, the distances R1 at each wide flow area are all equal to form a reference first reference circle; the distances R3 at each narrow flow area are all equal to form a reference second reference circle; the distances R2 at each wide and narrow flow area are equal to form a reference third reference circle.

Further, the flange structure is an upper flange.

According to another aspect of the present invention, a pump body assembly is provided that includes a flange structure.

Further, the pump body assembly still includes: a rotating shaft; the limiting plate is provided with a limiting plate exhaust hole; the cylinder jacket, the cylinder jacket has the cylinder jacket exhaust hole, and flange structure, limiting plate and cylinder jacket are passed in proper order to the pivot, and cylinder jacket exhaust hole, limiting plate exhaust hole and flange structure's amortization recess intercommunication.

Further, the cylinder liner has volume chamber pump body subassembly still includes: the cylinder is rotatably arranged in the volume cavity, and a piston hole is formed in the cylinder along the radial direction of the cylinder; the piston, the piston has the sliding hole, and at least a part of pivot wears to establish in the sliding hole, and the piston is along with the pivoted in-process of pivot rotation, and the piston slides in the piston hole for the pivot, and the cylinder synchronous revolution.

Further, the limiting plate exhaust hole is a plurality of, and a plurality of limiting plate exhaust holes interval sets up.

Further, the sizes of the at least two limiting plate exhaust holes are different.

Further, the cylinder jacket exhaust hole is a plurality of, and the cylinder jacket has a plurality of middle chambeies, and each middle chamber all communicates through the volume chamber of the cylinder jacket exhaust hole that corresponds and cylinder jacket, and the cylinder jacket still has a plurality of cylinder jacket intercommunicating pores with each middle chamber intercommunication, and a plurality of cylinder jacket intercommunicating pores set up with a plurality of limiting plate exhaust hole one-to-one.

Further, at least two of the plurality of cylinder liner exhaust holes are different in size; and/or the intermediate cavities are not communicated with each other; and/or at least two of the plurality of cylinder liner communication holes are different in size.

Further, the limiting plate exhaust holes and the flange exhaust holes of the flange structure are arranged at intervals in the circumferential direction of the flange structure.

According to another aspect of the present invention, there is provided a fluid machine including a pump body assembly.

By applying the technical scheme of the invention, one side of the flange structure, which faces to the cylinder sleeve, is provided with the silencing groove, the silencing groove extends along the circumferential direction of the flange structure, and the flange structure also comprises a flange exhaust hole which is communicated with the silencing groove; the outer peripheral face of the flange structure is provided with a plurality of connecting bosses extending out along the radial direction of the flange structure, and the plurality of connecting bosses are arranged along the circumferential interval of the flange structure so as to form a clearance concave part between two adjacent connecting bosses.

From the above description, it can be seen that, in the above embodiments of the present invention, the circumferentially extending sound deadening groove is disposed on one side of the flange structure, so that the flange structure has a sound deadening function, and the circumferentially extending sound deadening groove increases a flow path of gas, thereby effectively reducing noise generated by gas flow. The outer peripheral surface of the flange structure is provided with a plurality of connecting bosses to form a clearance concave part, so that the effects of vibration reduction and noise reduction are achieved. The present rotary cylinder compressor needs to be used with the muffler in a matched mode to reduce noise, and the flange structure is low in installation strength and easy to generate vibration noise.

Specifically, through the amortization recess that sets up circumference extension in the side of flange structure, gaseous one end that enters into the inside back edge amortization recess of amortization recess flows to the other end, reduces aerodynamic noise to make flange structure have the sound-deadening function. The flange structure has a supporting function, a plurality of connecting bosses are arranged at intervals on the outer peripheral surface of the flange structure, a clearance concave part is formed between the two connecting bosses, and when the flange structure is installed, the flange structure is installed through the connecting bosses on the outer peripheral surface, so that the installation is more stable, and the vibration noise is reduced. So as to achieve the effect of reducing noise.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:

FIG. 1 is a schematic view of the mounting relationship of a pump body assembly according to the present invention; and

figure 2 shows a cross-sectional view of the cylinder liner of figure 1;

figure 3 shows a schematic view of the cylinder liner of figure 1;

FIG. 4 is a schematic view of the flange structure of the present invention with sound attenuation grooves in end-to-end communication;

FIG. 5 is a schematic view showing a structure of a flange provided with a silencing groove, wherein the silencing groove is provided with a blocking structure between the head and the tail and is provided with six connecting bosses;

FIG. 6 shows a schematic view of the connection boss of FIG. 5;

FIG. 7 shows a cross-sectional view of the upper flange of FIG. 1;

figure 8 shows a schematic view of a limiting plate of the invention;

FIG. 9 is a schematic view showing the relationship of the distance between the central axis of the flange structure of the present invention and the noise-deadening groove;

fig. 10 shows a schematic view of a flange structure of the present invention having three coupling bosses.

Wherein the figures include the following reference numerals:

10. a cylinder; 20. a piston; 30. a rotating shaft; 40. a cylinder liner; 4011. a cylinder liner communication hole; 4012. a cylinder sleeve exhaust hole; 4013. a middle cavity; 50. an upper flange; 5011. a flange vent hole; 5021. a blocking structure; 5031. a silencing groove; 5051. connecting the bosses; 5061. welding spots; 5071. a journal; 70. an upper limiting plate; 7011. and a limiting plate exhaust hole.

Detailed Description

It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.

It is noted that, unless otherwise indicated, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

In the present invention, unless specified to the contrary, use of the terms of orientation such as "upper, lower, top, bottom" or the like, generally refer to the orientation as shown in the drawings, or to the component itself in a vertical, perpendicular, or gravitational orientation; likewise, for ease of understanding and description, "inner and outer" refer to inner and outer relative to the profile of the components themselves, but the above directional terms are not intended to limit the invention.

The invention provides a flange structure, a pump body assembly and a fluid machine, and aims to solve the problems that in the prior art, a flange structure does not have a noise reduction function and is easy to generate vibration noise in the operation process of a rotary cylinder compressor.

The fluid machine includes a pump body assembly described below, in which a flange structure described below is a part of the pump body assembly described below. In particular, the fluid machine is a compressor. Further, the compressor is a rotary cylinder compressor.

As shown in fig. 4 to 7, a noise-reducing groove 5031 is formed in one side of the flange structure facing the cylinder liner 40, the noise-reducing groove 5031 extends along the circumferential direction of the flange structure, the flange structure further includes a flange exhaust hole 5011, and the flange exhaust hole 5011 is communicated with the noise-reducing groove 5031; the outer peripheral surface of the flange structure has a plurality of connection bosses 5051 extending in the radial direction of the flange structure, the connection bosses 5051 are provided in plurality, and the plurality of connection bosses 5051 are provided at intervals in the circumferential direction of the flange structure to form a clearance recess between two adjacent connection bosses 5051.

From the above, it can be seen from the above description that in the above embodiment of the present invention, the circumferentially extending noise reduction groove 5031 is provided at one side of the flange structure, so that the flange structure has the noise reduction function, and the circumferentially extending noise reduction groove 5031 increases the flow path of the gas, thereby effectively reducing the noise of the gas flow. The outer peripheral surface of the flange structure is provided with a plurality of connecting bosses 5051 to form a clearance concave part, so that the effects of vibration reduction and noise reduction are achieved.

Specifically, by providing the circumferentially extending noise-reduction groove 5031 on the side of the flange structure, the gas flows along one end of the noise-reduction groove 5031 toward the other end after entering the interior of the noise-reduction groove 5031, thereby reducing aerodynamic noise, and enabling the flange structure to have a noise-reduction function. The flange structure has a supporting function, a plurality of connecting bosses 5051 arranged at intervals are arranged on the outer peripheral surface of the flange structure, a clearance concave part is formed between the two connecting bosses 5051, when the flange structure is installed, the flange structure is installed through the connecting bosses 5051 on the outer peripheral surface, so that the installation is more stable, the vibration noise is reduced, and the effect of reducing the noise is achieved.

In the present invention, the muffling grooves 5031 on the flange structure may or may not be connected to each other, so that the noise of the flange structure can be reduced by the muffling grooves 5031. Specifically, when the muffling groove 5031 is not communicated, a blocking structure 5021 is formed between the head and the tail of the muffling groove 5031, so that the gas entering the interior of the muffling groove 5031 flows along a directional path, which can enhance the noise reduction effect, and meanwhile, the blocking structure 5021 can increase the rigidity of the flange structure and improve the stability of the flange structure.

As shown in fig. 5, the distance between two adjacent connection bosses 5051 is equal. When the connecting bosses 5051 are arranged at equal intervals along the circumferential direction of the flange structure, the flange structure is stressed uniformly, concentrated stress is reduced, and vibration noise can be reduced stably in installation of the flange structure.

It should be noted that, distances between two adjacent connection bosses 5051 may also be unequal, and shapes of the connection bosses 5051 may be at least partially the same or all different, and are not listed here because there are many combination forms. The distance between two connecting bosses 5051 is based on the fact that a slight difference may exist between the shapes of two adjacent connecting bosses 5051, specifically, the concentrated stress during installation of the flange structure can be reduced, and the stability of installation is enhanced.

As shown in fig. 6, in the axial direction of the flange structure, connection bosses 5051 extend to both ends of the outer peripheral surface of the flange structure. The connecting bosses 5051 extend to two ends of the outer peripheral surface of the flange structure to increase the contact area between the connecting bosses 5051 and the flange structure, reduce concentrated stress, improve the stability of flange structure installation in the operation process of the rotary cylinder compressor and avoid vibration noise.

Specifically, each connecting boss 5051 is provided with at least one welding point 5061, and each connecting boss 5051 is provided with at least one welding point 5061, so as to enhance the stability of welding, and the more welding points, the higher the stability of the corresponding connecting boss 5051.

It should be noted that the connecting boss 5051 is not limited to be welded by the welding point 5061, but may be welded by a welding rod, so as to achieve the effects of stabilizing the flange structure and reducing vibration noise.

Depending on the number of connection bosses 5051, the present application provides the embodiment of fig. 5 with six connection bosses 5051. In addition, the embodiment of fig. 10 is provided in which there are three connection bosses 5051. Of course, the number of the connecting bosses 5051 may be two, four, five, etc., which are not listed here because of the many alternatives.

As shown in fig. 4 to 5, the side wall of the noise-reducing groove 5031 has a plurality of rib-like structures protruding toward the central axis of the flange structure, and the plurality of rib-like structures are arranged at intervals along the side wall of the noise-reducing groove 5031, so that the noise-reducing groove 5031 has alternately arranged wide flow areas and narrow flow areas.

Specifically, the noise-canceling recess 5031 is internally formed with wide and narrow flow-passing regions alternately arranged by a plurality of rib-like structures provided at intervals on the side wall of the noise-canceling recess 5031. When the gas flows into the silencing groove 5031, the gas is throttled and expanded for multiple times when passing through a plurality of wide flow passing regions and narrow flow passing regions arranged at intervals, so as to reduce noise.

In the invention, the number of the rib-shaped structures is more than 3 and less than 5. The plurality of ribs form the muffling grooves 5031 with wide flow areas and narrow flow areas alternately arranged to increase the throttling and expanding times, and it should be noted that the throttling and expanding times are not as many as possible, and when the number of ribs is greater than 3 and less than 5, the muffling function is achieved. In this embodiment, the number of rib-like structures is 3.

It should be noted that the distance between the central axes of the rib structures and the flange structure may be equal. The plurality of rib structures are disposed inside the noise reduction groove 5031 with the central axis of the flange structure as the center, and are equidistant from the central axis of the flange structure, so as to enhance the noise reduction effect. Of course, not all of the ribs need be equidistant from the central axis of the flange structure. The distance between the central axes of different rib-shaped structures and flange structures can be partially different or totally different, and the distances are not listed, and the distances between the central axes of the rib-shaped structures and the flange structures are reasonably set on the basis of realizing the silencing function.

As shown in fig. 1, 2, and 7, the flange structure has a flange hole, the flange hole is disposed eccentrically from the central axis of the flange structure, the middle portion of the flange structure has a journal 5071, the journal 5071 is formed by a portion having the noise reduction groove 5031 formed therein, the flange hole penetrates an axial end face of the journal 5071, and an outer circumference of the journal 5071 is coaxial with the outer circumference of the flange structure.

Particularly, the journal 5071 has a flexible supporting function, and can reduce concentrated stress, reduce abrasion of a flange structure and improve stability of the flange structure.

As shown in fig. 7, the side of the journal 5071 facing away from the cylinder liner 40 has a convex ring structure protruding from the end face of the flange structure so that the total height H in the axial direction of the flange structure is greater than the height H1 between the end faces in the axial direction of the flange structure, and the height H2 of the sound-deadening groove 5031 in the axial direction of the flange structure is smaller than the height H1 between the end faces in the axial direction of the flange structure.

Specifically, when the height H2 in the axial direction of the flange structure is greater than H1, the depth of the sound-deadening groove 5031 at this time is sufficiently large to ensure that the gas entering the inside of the sound-deadening groove 5031 can flow inside the sound-deadening groove 5031 and reduce noise. When the height H2 in the axial direction of the flange structure is smaller than H1, the depth of the noise reduction groove 5031 is too small to effectively reduce noise.

Note that 0.5H < H1<0.9H, and 0.3H < H2< 0.7H. When the relationship between the height H1 between the two axial end faces of the flange structure and the height H2 of the flange structure in the axial direction with respect to the total height H of the flange structure in the axial direction is maintained within the above range, noise can be effectively reduced, concentrated stress can be reduced, abrasion can be reduced, and stability can be improved.

As shown in fig. 7, the side wall thickness L1 of the flange structure and the end face thickness L2 of the flange structure satisfy the following relationship: 0.05H < L1< 0.25H; 0.1H < L2< 0.4H.

Specifically, when the side wall thickness L1 of the flange structure is too small, the rigidity of the flange structure is affected, and when the side wall thickness L1 of the flange structure is too large, the noise reduction effect is affected; when the end face thickness L2 of flange structure was too little, influenced the rigidity of flange structure, when the end face thickness L2 of flange structure was too big, influenced the noise cancelling effect, and noise cancelling effect can be guaranteed to reasonable end face thickness.

As shown in fig. 7, the side wall of the noise cancellation groove 5031 has a rib structure projecting toward the central axis of the flange structure, and the relationship between the minimum thickness L3 of the axial end face of the journal 5071 and the distance R3 between the rib structure and the center k2 of the journal 5071 is 0.05H < L3< R3.

Specifically, the rib structure influences the throttling expansion of the high-pressure gas, and the reasonable minimum thickness of the axial end face of the shaft neck 5071 and the distance R3 between the rib structure and the center k2 of the shaft neck 5071 can ensure the structural rigidity of the flange and enhance the noise reduction effect.

As shown in fig. 9, the eccentricity e is provided between the center k2 of the journal 5071 and the center k1 of the flange shaft hole of the flange structure, the distance between the center k1 of the flange shaft hole of the flange structure and the outer side groove wall of the noise reduction groove 5031 is R1, the distance between the rib structure and the center k2 of the journal 5071 is R3, the distance from the center k2 of the journal 5071 to the inner side groove wall of the noise reduction groove 5031 is R2, and the following relationships among R1, R2 and R3 are satisfied: 0.1< (R1-R2)/(R3-R2) < 0.4. In this example, 0.15< (R1-R2)/(R3-R2) < 0.25.

The flange structure of the present invention is the upper flange 50.

As shown in fig. 9, the distances R1 at each wide flow area are all equal to form a reference first reference circle; the distances R3 at each narrow flow area are all equal to form a reference second reference circle; the distances R2 at each wide and narrow flow area are equal to form a reference third reference circle.

As shown in fig. 1 to fig. 2, the pump body assembly further includes a rotating shaft 30, a limiting plate and a cylinder liner 40, the limiting plate has a limiting plate exhaust hole 7011, the cylinder liner 40 has a cylinder liner exhaust hole 4012, the rotating shaft 30 sequentially passes through the flange structure, the limiting plate and the cylinder liner 40, and the cylinder liner exhaust hole 4012, the limiting plate exhaust hole 7011 and the noise reduction groove 5031 of the flange structure are communicated. In the present embodiment, the stopper plate is an upper stopper plate 70.

Of course, if the pump body assembly of design is when lower exhaust structure, the flange structure can be lower flange, and the limiting plate can be lower limiting plate.

Specifically, the gas flows through the cylinder liner exhaust holes 4012 and the limiting plate exhaust holes 7011 in sequence, enters the noise reduction groove 5031 of the flange structure, is subjected to multiple throttling expansions in the noise reduction groove 5031 to achieve the noise reduction and reduction effects, and is then discharged through the flange exhaust hole 5011.

The limiting plate vent holes 7011 and the flange vent holes 5011 of the flange structure are arranged at intervals in the circumferential direction of the flange structure. In fig. 4 and 5, the exhaust holes 7011 of the limiting plate are staggered from the exhaust holes 5011 of the flange structure, so that the high-pressure gas entering from the exhaust holes 7011 of the limiting plate cannot be directly exhausted from the exhaust holes 5011 of the flange structure, but flows inside the silencing groove 5031 for a certain distance, then is throttled and expanded for multiple times in the silencing groove 5031 to achieve the effects of noise reduction and silencing, and then is exhausted through the exhaust holes 5011 of the flange structure.

It should be noted that, the sound-deadening groove 5031 of the flange structure has a plurality of different structures according to the different positions and angles of the blocking structure 5021, and since the blocking structure 5021 may be at a plurality of different angles, or may be disposed at any position of the sound-deadening groove 5031, specific embodiments of combinations of different positions and angles of the blocking structure 5021 are not listed.

As shown in fig. 1 to 3, in the present invention, a plurality of cylinder liner exhaust holes 4012 are provided, the cylinder liner 40 has a plurality of intermediate chambers 4013, each intermediate chamber 4013 communicates with a volume chamber of the cylinder liner 40 through a corresponding cylinder liner exhaust hole 4012, the cylinder liner 40 further has a plurality of cylinder liner communication holes 4011 communicating with each intermediate chamber 4013, a plurality of stopper plate exhaust holes 7011 are provided, and the plurality of cylinder liner communication holes 4011 and the plurality of stopper plate exhaust holes 7011 are provided in one-to-one correspondence.

Specifically, a plurality of cylinder liner exhaust holes 4012 and a plurality of intermediate chambers 4013 are provided inside the cylinder liner 40, the plurality of cylinder liner exhaust holes 4012 can increase exhaust efficiency, the plurality of cylinder liner exhaust holes 4012 discharge gas inside the volume chamber into the intermediate chamber 4013, the intermediate chamber 4013 has a buffering effect, and then the gas inside the intermediate chamber 4013 is discharged into the silencing groove 5031 through the plurality of cylinder liner communication holes 4011 and the plurality of stopper plate exhaust holes 7011 in sequence. The plurality of cylinder liner exhaust holes 4012 expedites the discharge of gases, while the plurality of intermediate chambers 4013 function as a buffer gas.

Further, at least two of the stopper plate exhaust holes 7011 are different in size, at least two of the cylinder liner exhaust holes 4012 of the plurality of cylinder liner exhaust holes 4012 are different in size, the respective intermediate chambers 4013 are not communicated with each other, and at least two of the cylinder liner communication holes 4011 of the plurality of cylinder liner communication holes 4011 are different in size.

In the embodiment shown in fig. 3, there are two cylinder liner exhaust ports 4012, and one larger and one smaller cylinder liner exhaust port 4012 may also be a pressure relief port. Since the cylinder liner communication holes 4011 need to correspond one-to-one to the stopper plate exhaust holes 7011, the two cylinder liner communication holes 4011 are also large and small.

Of course, the two intermediate chambers 4013 can be connected to each other, so that the flow path of the gas can be increased, and the gas can be properly arranged according to the requirement.

As shown in fig. 4 to 5, the limit plate exhaust hole 7011 and the flange exhaust hole 5011 of the flange structure are provided at an interval in the circumferential direction of the flange structure.

Specifically, the limiting plate exhaust holes 7011 and the flange exhaust holes 5011 are circumferentially spaced apart from each other, and when gas flows through the limiting plate exhaust holes 7011 and enters the inside of the sound deadening channel, the gas flows from the limiting plate exhaust holes 7011 to the flange exhaust holes 5011 and is then discharged through the flange exhaust holes 5011. At this time, the gas may be throttled and expanded several times inside the muffling groove 5031 to reduce noise and muffle sound.

As shown in fig. 1 to 2, in the present invention, the pump body assembly further includes a cylinder 10 and a piston 20, the cylinder 10 is rotatably disposed in the volume cavity of the cylinder sleeve 40, a piston hole is radially opened on the cylinder 10, the piston 20 has a sliding hole, at least a portion of the rotating shaft 30 penetrates the sliding hole, during the rotation of the piston 20 along with the rotating shaft 30, the piston 20 slides in the piston hole relative to the rotating shaft 30, and the cylinder 10 rotates synchronously.

From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:

the circumferentially extending noise reduction groove 5031 is arranged on one side of the flange structure, so that the existing flange structure has a noise reduction function, and the circumferentially extending noise reduction groove 5031 enlarges the flow path of the gas, and effectively reduces the noise of the gas flow. The outer peripheral surface of the flange structure is provided with a plurality of connecting bosses 5051 to form a clearance concave part, so that the effects of vibration reduction and noise reduction are achieved. The present rotary cylinder compressor needs to be used with the muffler in a matched mode to reduce noise, and the flange structure is low in installation strength and easy to generate vibration noise.

Specifically, by providing the circumferentially extending sound attenuation groove 5031 on the side of the flange structure, the gas flows along one end of the sound attenuation groove 5031 to the other end after entering the interior of the sound attenuation groove 5031, thereby reducing the aerodynamic noise, and enabling the flange structure to have a sound attenuation function. The flange structure has a supporting function, a plurality of connecting bosses 5051 arranged at intervals are arranged on the outer peripheral surface of the flange structure, a clearance concave part is formed between the two connecting bosses 5051, and when the flange structure is installed, the flange structure is installed through the connecting bosses 5051 on the outer peripheral surface, so that the installation is more stable, and the vibration noise is reduced. So as to achieve the effect of reducing noise.

It is to be understood that the above-described embodiments are only a few, but not all, embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, shall fall within the protection scope of the present invention.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments according to the present application. As used herein, the singular is intended to include the plural unless the context clearly dictates otherwise, and it should be further understood that the terms "comprises" and/or "comprising," when used in this specification, specify the presence of features, steps, operations, devices, components, and/or combinations thereof.

It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the application described herein are capable of operation in sequences other than those illustrated or described herein.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A flange structure is characterized in that a flange is arranged on a flange body,

one side, facing a cylinder sleeve (40), of the flange structure is provided with a noise reduction groove (5031), the noise reduction groove (5031) extends along the circumferential direction of the flange structure, the flange structure further comprises a plurality of flange exhaust holes (5011), the flange exhaust holes (5011) are communicated with the noise reduction groove (5031), the side wall of the noise reduction groove (5031) is provided with a rib-shaped structure protruding towards the central axis of the flange structure, and the plurality of rib-shaped structures are arranged at intervals along the side wall of the noise reduction groove (5031) so that the noise reduction groove (5031) is provided with alternately arranged wide flow passing areas and narrow flow passing areas; after entering the interior of the noise reduction groove (5031), the gas flows along one end of the noise reduction groove (5031) to the other end;

the outer peripheral surface of the flange structure is provided with a plurality of connecting bosses (5051) extending along the radial direction of the flange structure, the connecting bosses (5051) are arranged at intervals along the circumferential direction of the flange structure, and a clearance concave part is formed between every two adjacent connecting bosses (5051).

2. The flange structure according to claim 1, wherein said muffling recess (5031) communicates end-to-end.

3. The flange structure according to claim 1, wherein the ends of the noise-canceling grooves (5031) are not communicated to form a blocking structure (5021) between the ends of the noise-canceling grooves (5031).

4. The flange structure according to claim 1, wherein the distance between adjacent two of said connecting projections (5051) is equal.

5. The flange structure according to claim 1, wherein the connection boss (5051) extends to both ends of the outer circumferential surface of the flange structure in the axial direction of the flange structure.

6. A flange structure according to claim 1, characterized in that each of said connecting projections (5051) is provided with at least one welding point (5061).

7. A flange structure according to any one of claims 1 to 6, characterized in that the number of web-like structures is more than 3 and less than 5.

8. The flange structure according to any one of claims 1 to 6, wherein the flange structure has a flange hole which is provided eccentrically to a central axis of the flange structure, a journal (5071) is provided in a middle portion of the flange structure, the journal (5071) is constituted by a portion in which the noise cancellation groove (5031) is opened, the flange hole penetrates an axial end face of the journal (5071), and an outer circumference of the journal (5071) is coaxial with the outer circumference of the flange structure.

9. The flange structure according to claim 8, wherein a side of the journal (5071) facing away from the cylinder liner (40) has a projecting ring structure projecting from an end face of the flange structure such that a total height H in an axial direction of the flange structure and the journal (5071) is greater than a height H1 between both end faces in the axial direction of the flange structure, and a height H2 of the noise cancellation groove (5031) in the axial direction of the flange structure is smaller than a height H1 between both end faces in the axial direction of the flange structure.

10. The flange structure according to claim 9,

0.5H < H1< 0.9H; and/or

0.3H<H2<0.7H。

11. The flange structure according to claim 10,

0.65H < H1< 0.75H; and/or

0.4H<H2<0.6H。

12. The flange structure according to claim 9, wherein the side wall thickness L1 of the flange structure and the end face thickness L2 of the flange structure satisfy the following relationship:

0.05H<L1<0.25H；

0.1H<L2<0.4H。

13. the flange structure according to claim 9, wherein the side wall of the noise-damping groove (5031) has a bead-like structure protruding toward the central axis of the flange structure, and the relationship between the minimum thickness L3 of the axial end face of the journal (5071) and the distance R3 between the bead-like structure and the center k2 of the journal (5071) is 0.05H < L3< R3.

14. The flange structure according to any one of claims 1 to 6, wherein a journal (5071) is disposed in the middle of the flange structure, an eccentric amount e is provided between a center k2 of the journal (5071) and a flange shaft hole center k1 of the flange structure, a distance between a flange shaft hole center k1 of the flange structure and an outer side groove wall of the noise reduction groove (5031) is R1, a distance from the rib structure to a center k2 of the journal (5071) is R3, a distance from the center k2 of the journal (5071) to an inner side groove wall of the noise reduction groove (5031) is R2, and R1, R2 and R3 satisfy the following relationships:

0.1<（R1-R2）/（R3-R2）<0.4。

15. the flange structure of claim 14, wherein 0.15< (R1-R2)/(R3-R2) < 0.25.

16. The flange structure according to claim 14,

distances R1 at each of the wide flow passing regions are all equal to form a reference first reference circle;

the distances R3 at each narrow flow-passing region are all equal to form a reference second reference circle;

distances R2 at each of the wide and narrow flow areas are equal to form a reference third reference circle.

17. A flange structure according to any one of claims 1-6, characterized in that the flange structure is an upper flange (50).

18. A pump body assembly, characterized by comprising a flange structure according to any one of claims 1 to 17.

19. The pump body assembly of claim 18, further comprising:

a rotating shaft (30);

a limiting plate having a limiting plate vent (7011);

cylinder jacket (40), cylinder jacket (40) have cylinder jacket exhaust hole (4012), pivot (30) pass in proper order the flange structure the limiting plate with cylinder jacket (40), cylinder jacket exhaust hole (4012) limiting plate exhaust hole (7011) with amortization recess (5031) intercommunication of flange structure.

20. The pump body assembly according to claim 19, characterized in that said cylinder liner (40) has a volume cavity, said pump body assembly further comprising:

the cylinder (10) is rotatably arranged in the volume cavity, and a piston hole is formed in the cylinder (10) along the radial direction of the cylinder;

the piston (20), the piston (20) has the sliding hole, at least a part of pivot (30) wear to establish in the sliding hole, in the piston (20) along with pivot (30) pivoted process, the piston (20) for pivot (30) slide in the piston hole, and cylinder (10) synchronous rotation.

21. The pump body assembly according to claim 19, wherein the stopper plate vent hole (7011) is provided in plurality, and the plurality of stopper plate vent holes (7011) are provided at intervals.

22. The pump body assembly according to claim 21, wherein at least two of the limit plate vent holes (7011) are of different sizes.

23. The pump body assembly according to claim 21, wherein the cylinder liner exhaust hole (4012) is plural, the cylinder liner (40) has a plurality of intermediate chambers (4013), each of the intermediate chambers (4013) communicates with the volume chamber of the cylinder liner (40) through the corresponding cylinder liner exhaust hole (4012), the cylinder liner (40) further has a plurality of cylinder liner communication holes (4011) communicating with each of the intermediate chambers (4013), and the plurality of cylinder liner communication holes (4011) are provided in one-to-one correspondence with the plurality of stopper plate exhaust holes (7011).

24. The pump body assembly according to claim 23,

at least two of the cylinder liner exhaust ports (4012) of the plurality of cylinder liner exhaust ports (4012) are different sizes; and/or

The intermediate cavities (4013) are not communicated with each other; and/or

At least two of the cylinder liner communication holes (4011) of the plurality of cylinder liner communication holes (4011) are different in size.

25. The pump body assembly according to claim 19, wherein the limit plate vent hole (7011) and the flange vent hole (5011) of the flange structure are provided at a spacing in a circumferential direction of the flange structure.

26. A fluid machine comprising a pump body assembly according to any one of claims 18 to 25.