CN204436791U - For compressor compressing mechanism and there is its compressor - Google Patents

Abstract

The utility model discloses a compression mechanism for a compressor and a compressor with the same. The compression mechanism comprises: a cylinder assembly and a bearing arranged at one axial end of the cylinder assembly. The cylinder assembly includes a cylinder with a compression cavity inside the cylinder , the bearing includes: a journal portion, a flange portion, and a plurality of first ribs, the flange portion is arranged between the journal portion and the cylinder assembly, and in the axial direction of the cylinder assembly, the flange portion includes a As for the opposite supporting part, each first reinforcing rib extends along the inner and outer direction and is arranged on the side of the supporting part away from the cylinder assembly, and a plurality of first reinforcing ribs are distributed at intervals in the circumferential direction of the supporting part. According to the compression mechanism of the utility model, the rigidity of the bearing can be effectively improved by arranging a plurality of first reinforcing ribs on the supporting part, so that the stress distribution of the bearing is more uniform, the material utilization rate of the bearing is improved, and the production cost of the bearing is reduced.

Description

Compression mechanism for compressor and compressor having same

technical field

The utility model relates to the field of compressor equipment, in particular to a compression mechanism for a compressor and a compressor with the same.

Background technique

The bearings in the compressor generally have two functions. On the one hand, they are arranged at both axial ends of the cylinder to define a compression chamber with the cylinder. On the other hand, they are used to support the crankshaft. It is pointed out in the related art Only when the bearing has sufficient rigidity can the compressor run normally and efficiently, and ensure that under the action of the pressure difference between the compression chamber and the outer shell cavity, the bearing will not produce excessive axial deformation, causing the compression mechanism to be stuck or Cause excessive running resistance; moreover, only when the bearing has sufficient rigidity can the pressure between the bearing and the cylinder end face be sufficient to avoid leakage between the compression chamber and the outer housing cavity; in addition, the bearing can only be Ensure that under the action of the unbalanced magnetic pull of the motor, the rotor will not produce excessive deformation and come into contact with the stator to cause abnormal noise. However, it is pointed out in the related art that the rigidity of the bearing can only be ensured if the shaft diameter part and the flat flange part of the bearing are designed thicker. , will lead to lower material utilization of the bearing and higher cost.

Utility model content

The utility model aims at at least solving one of the technical problems existing in the prior art. Therefore, the utility model is to provide a compression mechanism for a compressor, in which the bearings in the compression mechanism have good rigidity, high material utilization rate and low cost.

The utility model also proposes a compressor with the above compression mechanism.

The compression mechanism for a compressor according to the first aspect of the utility model includes: a cylinder assembly and a bearing arranged at one end of the cylinder assembly in the axial direction, the cylinder assembly includes a cylinder with a compression chamber inside the cylinder, and The bearing includes: a shaft neck; a flange part, the flange part is arranged between the shaft neck and the cylinder assembly, and in the axial direction of the cylinder assembly, the flange part includes the The axially opposite supporting portion of the cylinder assembly; and a plurality of first reinforcing ribs, each of which extends along the inner and outer directions and is arranged on a side of the supporting portion away from the cylinder assembly, the plurality of The first reinforcement ribs are distributed at intervals in the circumferential direction of the support portion.

According to the compression mechanism used in the compressor of the utility model, the rigidity of the bearing can be effectively improved by arranging a plurality of first reinforcing ribs on the supporting part, so that the stress distribution of the bearing is more uniform, the material utilization rate of the bearing is improved, and the bearing capacity is reduced. production cost.

Specifically, a slide groove extending radially along the cylinder is formed on the cylinder, and one of the plurality of first reinforcing ribs and the slide groove are within a radius of the cylinder. Set up relative.

Specifically, the width of the first reinforcing rib disposed opposite to the sliding vane groove in the radial direction of the cylinder is greater than the width of each of the remaining first reinforcing ribs in the plurality of first reinforcing ribs.

Specifically, a cavity is defined between every two adjacent first reinforcing ribs, and the cavity on both sides of the first reinforcing rib opposite to the slide slot in the radial direction of the cylinder The depth is smaller than the depth of the cavities defined between the remaining first ribs in the plurality of first ribs.

Specifically, an air suction hole communicating with the compression chamber is formed on the cylinder, and at least one of the plurality of first reinforcing ribs is aligned with the air suction hole on the axis of the cylinder. Up corresponds to the setting.

Specifically, an exhaust valve seat is provided on the support portion, and the first reinforcing rib is provided at both ends of the exhaust valve seat in the length direction.

Further, the bearing further includes: a second reinforcing rib, the second reinforcing rib is provided on a side of the supporting part away from the cylinder assembly and extends along the circumferential direction of the supporting part.

Specifically, the second reinforcing rib includes an inner peripheral reinforcing rib, and the inner peripheral reinforcing rib is connected between the journal portion and the supporting portion.

Specifically, along the direction from the inside to the outside, the axial thickness of the inner peripheral reinforcing rib gradually decreases.

Specifically, the second reinforcing rib includes a transitional reinforcing rib, and the transitional reinforcing rib is connected between the outer edge of the inner circumferential reinforcing rib and the inner end of the first reinforcing rib.

Specifically, the second reinforcing rib includes a peripheral reinforcing rib, and the peripheral reinforcing rib is arranged between the outer edge of the support part and the outer end of the first reinforcing rib.

Specifically, a through installation hole is formed on the outer peripheral reinforcing rib.

Specifically, in the radial direction of the supporting portion, the mounting holes are arranged corresponding to the first reinforcing ribs.

Specifically, in the axial direction of the cylinder assembly, the end surface of the installation hole on a side away from the cylinder assembly is located on the side of the first rib away from the cylinder assembly.

Optionally, a mounting boss protruding away from the cylinder assembly is formed on the outer peripheral reinforcing rib, and the mounting hole is formed on the mounting boss.

Optionally, a mounting sinker recessed toward the direction of the cylinder assembly is formed on the outer peripheral reinforcing rib, and the mounting hole is formed on the mounting sinker.

The compressor according to the second aspect of the utility model includes the compression mechanism for the compressor according to the first aspect of the utility model.

According to the compressor of the present invention, the overall performance of the compressor is improved by providing the compression mechanism for the compressor in the first aspect.

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

Description of drawings

Fig. 1 is a schematic diagram of a bearing according to an embodiment of the present invention;

2 is a schematic diagram of a compression mechanism according to an embodiment of the present invention;

3 is a schematic diagram of a compression mechanism according to another embodiment of the present invention;

Fig. 4 is a schematic diagram of a bearing according to another embodiment of the present invention;

Fig. 5 is a schematic diagram of a compression mechanism according to yet another embodiment of the present invention.

Reference signs:

1000: compression mechanism;

100: bearing;

1: journal;

2: flange part; 21: support part; 21a: first surface; 21b: second surface; 22: outer ring part;

3: The first rib;

4: second rib; 41: inner rib; 42: outer rib;

43: transition rib; 44: installation boss;

5: Mounting hole; 6: Exhaust valve seat; 7: Solder spot;

200: air cylinder; 201: compression chamber; 202: slide slot; 203: suction hole.

Detailed ways

Embodiments of the present invention are described in detail below, examples of which are shown in the drawings, wherein the same or similar reference numerals represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the figures are exemplary and are intended to explain the present invention, but should not be construed as limiting the present invention.

The following disclosure provides many different embodiments or examples for realizing different structures of the present invention. To simplify the disclosure of the present invention, components and arrangements of specific examples are described below. Of course, they are only examples, and the purpose is not to limit the utility model. Furthermore, the present invention may repeat reference numerals and/or letters in different instances. This repetition is for the purpose of simplicity and clarity and does not in itself indicate a relationship between the various embodiments and/or arrangements discussed. In addition, various specific process and material examples are provided herein, but one of ordinary skill in the art will recognize the applicability of other processes and/or the use of other materials.

A compression mechanism 1000 for a compressor according to an embodiment of the first aspect of the present invention will be described below with reference to FIGS. 1-5 . Specifically, the compressor (not shown) may also include a casing (not shown), a motor (not shown) and a crankshaft (not shown), wherein the casing may be formed substantially in a cylindrical shape The airtight container, the motor and the compression mechanism 1000 are all arranged in the casing, and are spaced apart in the axial direction of the casing, wherein the motor may include a rotor and a stator, one end of the crankshaft is fixed to the rotor, and the other end of the crankshaft runs through the compression mechanism 1000, in this way, when the motor is working, the rotor can drive the crankshaft to rotate to compress the refrigerant in the compression mechanism 1000.

As shown in Figures 1 and 2, the compression mechanism 1000 for a compressor according to the embodiment of the first aspect of the present invention includes: a cylinder assembly and a bearing 100 arranged at one axial end of the cylinder assembly, the cylinder assembly includes a cylinder 200, The cylinder 200 has a compression chamber 201 inside. Wherein, the compressor can be a single-cylinder compressor or a multi-cylinder compressor. When the compressor is a single-cylinder compressor, the cylinder assembly only includes one cylinder 200, and two axial ends of the cylinder 200 can be respectively provided with a bearing 100 to communicate with the cylinder. A compression chamber 201 is defined between the cylinders 200. When the compressor is a multi-cylinder compressor, the cylinder assembly may include a plurality of cylinders 200, and there may be a partition between every two adjacent cylinders 200. The plurality of cylinders 200 A bearing 100 can be provided at both axial ends, and two cylinders 200 at the axial ends define compression chambers 201 through partitions and bearings 100 respectively, and other cylinders 200 can define compression chambers 201 through partitions at their axial ends. The following description will be made only by taking the compressor as an example of a single-cylinder compressor. Of course, the compressor may also be a multi-cylinder compressor. Of course, the present invention is not limited thereto, and the bearing 100 can also be provided only at one axial end of the cylinder assembly, and at this time, other types of bearings can also be provided at the other end of the cylinder assembly.

Specifically, the bearing 100 includes a journal portion 1 and a flange portion 2, and the flange portion 2 is arranged between the journal portion 1 and the cylinder assembly. Referring to Fig. 1, the journal portion 1 can be formed into a substantially cylindrical shape, the flange portion 2 can be formed into a substantially disc shape, the journal portion 1 is arranged on the side of the flange portion 2 away from the cylinder 200, and can be obtained from the French The center of the end face of the flange part 2 away from the cylinder 200 extends toward the direction away from the cylinder 200. During assembly, the flange part 2 and the cylinder 200 can be assembled together by threaded fasteners (such as screws or bolts), etc. To fix the bearing 100 on the cylinder 200.

Wherein, in the axial direction of the cylinder assembly, the flange portion 2 includes a supporting portion 21 axially opposite to the cylinder assembly, that is to say, on a reference plane perpendicular to the central axis of the cylinder assembly, the flange portion 2 is aligned with the cylinder 200 The portion facing the cylinder assembly in the axial direction is the support portion 21 . For example, in the example of Fig. 2 and Fig. 3, the projection dimension of the flange part 2 on the reference plane is smaller than the projection dimension of the cylinder assembly on the reference plane, and at this moment the flange part 2 is all supporting parts 21, such as in Fig. 4 and Fig. 3 In the example of Fig. 5, the projection size of the flange part 2 on the reference plane is greater than the projection size of the cylinder assembly on the reference plane, and because the flange part 2 and the cylinder assembly are assembled coaxially, only the flange part 2 and The inner ring portion facing up and down of the cylinder assembly is the support portion 21 , while the outer ring portion 22 of the flange portion 2 is not facing the cylinder assembly up and down, so it is not the support portion 21 . Here, it should be noted that the direction "up and down" is understood in a broad sense, that is, it should be understood as a direction along the axis of the cylinder assembly.

In order to simplify the following description, with reference to FIG. 1, the side surface of the support portion 21 that is adjacent to and matched with the cylinder assembly is defined as the first surface 21a of the support portion 21, and the side opposite to the first surface 21a of the support portion 21 is defined as The surface, that is, the side surface of the support portion 21 away from the cylinder assembly is defined as the second surface 21b of the support surface.

Specifically, referring to FIG. 1 , the bearing 100 further includes a plurality of first reinforcing ribs 3, and each first reinforcing rib 3 is provided on the side of the support portion 21 away from the cylinder assembly, that is, each first reinforcing rib 3 is provided On the second surface 21b of the supporting part 21, for example, each first reinforcing rib 3 can be formed by extending from the second surface 21b of the supporting part 21 toward the direction away from the cylinder assembly, so that the height of each first reinforcing rib 3 is high Out of the height of the second surface 21b on both sides, that is to say, the distance between each first rib 3 and the first surface 21a is greater than the distance between the second surface 21b on both sides and the first surface 21a .

Further, each first reinforcing rib 3 extends along the inner and outer directions, for example, each first reinforcing rib 3 can extend along the radial direction of the flange part 2, that is to say, the extension line of the first reinforcing rib 3 can be the same as the normal The radial lines of the blue part 2 overlap and pass through the central axis of the bearing 100, and a plurality of first reinforcing ribs 3 are spaced apart in the circumferential direction of the supporting part 21, that is to say, every two adjacent first reinforcing ribs 3 The circumferential direction of the blue portion 2 is spaced at a certain distance. Here, it should be noted that “inner” can be understood as a direction toward the central axis of the bearing 100 , and the opposite direction is defined as “outer”, that is, a direction away from the central axis of the bearing 100 . Wherein, the first reinforcing rib 3 , the flange portion 2 and the journal portion 1 can be integrally cast and formed directly, so that the bearing 100 is easy to form and has high feasibility for mass production. Certainly, the present invention is not limited thereto, and each first reinforcing rib 3 may not extend along the radial direction of the flange portion 2 .

Therefore, the rigidity of the bearing 100 can be effectively improved by arranging a plurality of first ribs 3 to ensure that the bearing 100 is not prone to excessive axial deformation during the operation of the compressor, thereby ensuring the smooth operation of the compression mechanism 1000. There is no problem of jamming or excessive running resistance, and because the rigidity of the bearing 100 is high enough to ensure that the pressure between the bearing 100 and the end surface of the cylinder 200 is sufficient after a plurality of first ribs 3 are provided, thereby avoiding the compression mechanism 1000 has the problem of leakage, and in addition, it also avoids the problem of abnormal sound generated during the working process of the motor (as described below).

According to the compression mechanism 1000 for the compressor of the embodiment of the present invention, the rigidity of the bearing 100 can be effectively improved through a plurality of first ribs 3, so that the stress distribution of the bearing 100 is more uniform, so that the The lower bearing 100 can achieve the rigidity of the bearing in the related art, thereby effectively improving the material utilization rate of the bearing 100 and reducing the overall cost of the bearing 100 . In addition, the bearing 100 is easy to process and easy to popularize and apply.

Specifically, a slide groove 202 extending radially along the cylinder 200 and an air suction hole 203 communicating with the compression chamber 201 are formed on the cylinder 200 . Referring to Figure 2, Figure 3 and Figure 5, the cylinder 200 can be formed with a compression chamber hole penetrating in its axial direction, the compression chamber hole is used to define the compression chamber 201, and the sliding vane groove 202 can be formed along the side wall of the compression chamber hole Concave radially outwards of the cylinder 200, an exhaust hole (not shown) and an air suction hole 203 are further formed on the cylinder 200, the air suction hole 203 and the air exhaust hole are connected to the compression chamber 201 respectively, and the air suction The hole 203 and the exhaust hole are respectively disposed on two sides of the slide groove 202 and adjacent to the slide groove 202 .

In an embodiment of the present utility model, referring to FIG. 2 , one first rib 3 a among the plurality of first ribs 3 is arranged opposite to the slide groove 202 in the radial direction of the cylinder 200 . That is to say, there is a first reinforcing rib 3 a on the second surface 21 b of the corresponding bearing 100 at a position 180° apart from the slide slot 202 with the central axis of the cylinder 200 as the origin. In other words, on the reference plane, there is a projection of the first reinforcing rib 3 a and a projection of the slide slot 202 on the same diameter projection line of the cylinder 200 and on both sides of the central axis of the cylinder 200 .

Here, it should be noted that, for a high back pressure rotary compressor, when the crankshaft rotation angle is 0°, the pressure in the compression chamber 201 is the lowest, and at this time, the part of the bearing 100 opposite to the compression chamber 201 is in the compression chamber 201 deforms the most under the action of the pressure difference inside the shell, and the largest deformation occurs in the area on the bearing 100 that is radially opposite to the slide slot 202, so that when the area on the bearing 100 that is radially opposite to the slide slot 202 Setting the first reinforcing rib 3a at the position can effectively improve the deformation problem of the bearing 100 .

Preferably, referring to FIG. 2 , the width D1 of the first reinforcing rib 3 a disposed opposite to the sliding vane groove 202 in the radial direction of the cylinder 200 is greater than the width of each of the remaining first reinforcing ribs 3 in the plurality of first reinforcing ribs 3 , For example, it is larger than the width D2 of the first reinforcing rib 3 adjacent to it. Thus, the problem of deformation at the weak point of the bearing 100 can be further improved. Further, a cavity 2a is defined between every two adjacent first ribs 3, and the depth of the cavities 2a on both sides of the first rib 3a opposite to the slider groove 202 in the radial direction of the cylinder 200 is less than The depth of the cavity defined between the remaining first reinforcing ribs 3 among the plurality of first reinforcing ribs 3 . Thus, it can be ensured that the portion of the bearing 100 radially opposite to the vane groove 202 has a larger thickness and stronger rigidity, thereby further improving the deformation problem of the weak part of the bearing 100 and improving the operation reliability of the compressor.

Specifically, at least one first reinforcing rib 3 among the plurality of first reinforcing ribs 3 is arranged corresponding to the suction hole 203 in the axial direction of the cylinder 200 . Referring to FIG. 3 , on the reference plane, the projection of the suction hole 203 substantially coincides with the projection of at least one first rib 3 (such as the first rib 3b shown in FIG. 3 ), thereby improving the bearing 100 in The strength of this region, in turn, reduces compression mechanism 1000 leakage. Here, it can be understood that since the suction hole 203 of the cylinder 200 has a weakening effect on the local rigidity of the bearing 100, that is to say, the part of the bearing 100 corresponding to the suction hole 203 of the cylinder 200 is the area of the bearing 100 with the lowest contact pressure. Improving the rigidity of the bearing 100 in this area is beneficial to reduce the leakage problem caused by the pressure difference between the compression chamber 201 and the housing.

In one embodiment of the present utility model, with reference to Fig. 4 and Fig. 5, the cylinder assembly can exhaust gas through at least one of the two bearings 100 (the first bearing and the second bearing) at both axial ends of the cylinder assembly, that is to say , the cylinder assembly can exhaust gas only through the first bearing, the cylinder assembly can also exhaust gas only through the second bearing, and the cylinder assembly can also exhaust gas through both the first bearing and the second bearing. When the cylinder assembly exhausts air only through the first bearing, there is an exhaust valve seat 6 on the first bearing, and there is no exhaust valve seat 6 on the second bearing. When the cylinder assembly exhausts air only through the second bearing, the second bearing There is an exhaust valve seat 6 on the second bearing, and there is no exhaust valve seat 6 on the first bearing. When the cylinder assembly exhausts air through both the first bearing and the second bearing, the first bearing and the second All have exhaust valve seat 6 on the bearing.

Optionally, as shown in Figures 1 and 2, when the bearing 100 does not have the exhaust function, that is, when the bearing 100 does not have the exhaust valve seat 6, there may be multiple five) first reinforcing ribs 3 shown, and a plurality of first reinforcing ribs 3 can be evenly spaced and distributed in the circumferential direction of the bearing 100, wherein each first reinforcing rib 3 can extend radially along the bearing 100, In order to make the stress distribution of the bearing 100 more uniform.

Optionally, as shown in Fig. 4 and Fig. 5, when the bearing 100 has an exhaust function, that is, when the bearing 100 has an exhaust valve seat 6, the exhaust valve seat 6 is formed on the supporting part 21, and the exhaust valve Both ends of the seat 6 in the length direction are respectively provided with a first reinforcing rib 3c. Specifically, the valve seat can be formed by recessing the second surface 21b of the bearing 100 toward the direction of the cylinder assembly, and the exhaust valve seat 6 has a first rib 3c at both ends of the bearing 100 in the circumferential direction, so that it can effectively The rigidity of the exhaust valve seat 6 of the bearing 100 is improved, the deformation problem of the exhaust valve seat 6 is improved, and the exhaust reliability of the exhaust valve seat 6 is ensured.

Specifically, the bearing 100 further includes: a second reinforcing rib 4 . The second reinforcing rib 4 is provided on a side of the supporting portion 21 away from the cylinder assembly and extends along the circumferential direction of the supporting portion 21 . For example, in the example shown in Fig. 1 and Fig. 4, the second reinforcing rib 4 is provided on the second surface 21b of the supporting part 21, and the second reinforcing rib 4 can face away from the direction of the cylinder assembly from the second surface 21b of the supporting part 21. Extending, the second reinforcing rib 4 extends along the circumferential direction of the supporting part 21 , for example, the second reinforcing rib 4 may be formed in an arc shape, a circular ring or a discontinuous circular ring concentric with the outer edge of the supporting part 21 .

Specifically, the second reinforcing rib 4 includes an inner peripheral reinforcing rib 41, which is connected between the journal portion 1 and the support portion 21, and the inner peripheral reinforcing rib 41 can face away from the cylinder assembly from the second surface 21b. The direction is convex. For example, in the example shown in FIG. 1 and FIG. 4 , the inner peripheral reinforcing rib 41 may extend from the journal portion 1 to the second surface 21b of the support portion 21, thereby connecting between the shaft diameter portion and the support portion 21, preferably along From the inside to the outside, the axial thickness of the inner peripheral rib 41 gradually decreases, that is to say, the cross section of the inner peripheral rib 41 is formed into a triangle, in other words, the inner peripheral rib 41 can be understood as being arranged on the shaft Chamfer at the base of the neck.

Thus, the axial deformation of the bearing 100 under the pressure difference between the compression chamber 201 and the shell can be significantly reduced, thereby reducing the running resistance of the crankshaft and preventing the compressor from being stuck. In addition, the inner peripheral ribs 41 can also effectively improve the ability of the compression mechanism 1000 to resist the unbalanced magnetic pull of the motor, thereby reducing the radial deformation of the rotor to prevent the abnormal sound generated by the contact between the stator and the rotor, and at the same time reduce the The radial deformation of the compression mechanism 1000 is avoided, thereby avoiding the vibration problem caused by the excessive radial deformation of the compression mechanism 1000.

In addition, referring to Fig. 4 and Fig. 5, on the reference plane, the projected area of the bearing 100 is larger than the projected area of the cylinder assembly, at this time, the bearing 100 can be welded (for example, through the welding spot 7 shown in Fig. 4) to the housing However, when the bearing 100 is fixed on the cylinder 200 only by the supporting part 21, setting the inner peripheral rib 41 and the transition rib 43 on the bearing 100 can effectively improve the compression mechanism 1000. The overall rigidity can effectively improve the reliability of the compressor and reduce the vibration and noise of the compressor. Wherein, "overall rigidity of the compression mechanism 1000" refers to the ability of the compression mechanism 1000 to resist unbalanced magnetic pull.

Further, the second rib 4 may also include a transition rib 43 connected between the outer edge of the inner peripheral rib 41 and the inner end of the first rib 3 . Referring to Fig. 1 and Fig. 2, the inner end of the transition rib 43 is connected with the inner peripheral rib 41, the outer end of the transition rib 43 is connected with the inner end of the first rib 3, and the transition rib 43 can be formed by the second surface. 21b protrudes toward the direction away from the cylinder assembly, so that the transition rib 43 can assist the inner peripheral rib 41 to further improve the overall rigidity of the compression mechanism 1000, thereby improving the reliability of the compressor and reducing the vibration and abnormal sound of the compressor .

Further, as shown in FIGS. 1-5 , the second reinforcing rib 4 may also include a peripheral reinforcing rib 42, and the peripheral reinforcing rib 42 is arranged between the outer edge of the supporting portion 21 and the outer end of the first reinforcing rib 3, Therefore, the outer peripheral reinforcing rib 42 can increase the rigidity of the edge of the supporting portion 21 and further improve the overall performance of the bearing 100 .

Optionally, the peripheral reinforcing rib 42 is formed with a through installation hole 5 . Referring to Fig. 1 and Fig. 2, the cylinder assembly and the bearing 100 can be fixed together by threaded fasteners, at this time, the bearing 100 is formed with a plurality of mounting holes 5, and the plurality of mounting holes 5 are all formed on the outer peripheral rib 42 , a plurality of installation holes 5 can be distributed at intervals in the circumferential direction of the support portion 21, thus, the rigidity of the area between the installation holes 5 can be effectively improved, so that when the bearing 100 and the cylinder are connected by threaded fasteners (such as screws) After the components are connected together, the contact pressure between the bearing 100 and the cylinder component is guaranteed, which improves the connection reliability and sealing tightness of the bearing 100, thereby avoiding the pressure difference between the compression chamber 201 and the housing. leakage problem.

Specifically, in the radial direction of the support portion 21 , the mounting holes 5 are provided corresponding to the first reinforcing ribs 3 . Referring to Fig. 1, the mounting hole 5 can be located at the junction of the first reinforcing rib 3 and the peripheral reinforcing bar, so that the local rigidity of the mounting hole 5 can be further improved, the connection reliability of the threaded fastener can be further improved, and the compression cavity can be further improved. Leakage between 201 and the shell. In addition, the bearing 100 can be formed by casting process, and then the outer peripheral rib 42 can be machined to meet the precision requirements of the surface of the mounting hole 5, thereby reducing the processing cost and improving the processing effect.

Preferably, referring to FIG. 1 , in the axial direction of the cylinder assembly, the end face of the installation hole 5 on the side away from the cylinder assembly is located on the side of the first rib 3 away from the cylinder assembly, that is, the height of the installation hole 5 is high At the height of the first rib 3, in other words, the distance between the end surface of the mounting hole 5 on the side away from the cylinder assembly and the first surface 21a is greater than the distance between the end surface of the first rib 3 on the side away from the cylinder assembly and the first surface 21a the distance between. As a result, the machining process is further facilitated, the processing cost is reduced, and the processing effect is improved.

Further, referring to FIG. 3 , a mounting boss 44 protruding toward a direction away from the cylinder assembly may be formed on the outer peripheral rib 42 , for example, the mounting boss 44 may protrude from the second surface 21b of the bearing 100 toward a direction away from the cylinder assembly. Therefore, the height of the mounting boss 44 is higher than the height of the outer peripheral reinforcing rib 42, in other words, the distance between the end surface of the mounting boss 44 on the side away from the cylinder assembly and the first surface 21a is greater than that of the outer peripheral reinforcing rib 42 away from the cylinder. The distance between the end surface on one side of the assembly and the first surface 21a, preferably, in the axial direction of the cylinder assembly, the end surface on the side away from the cylinder assembly of the mounting boss 44 is located at one side of the first rib 3 away from the cylinder assembly. side, that is to say, the height of the mounting boss 44 is also higher than the height of the first rib 3, in other words, the distance between the end surface of the mounting boss 44 on the side away from the cylinder assembly and the first surface 21a is greater than that of the first reinforcing rib 3. The distance between the end surface of the rib 3 on the side away from the cylinder assembly and the first surface 21a, at this time, the installation hole 5 is formed on the installation boss 44 .

Or alternatively, the outer peripheral rib 42 can also be formed with a mounting sinking recessed toward the direction of the cylinder assembly, for example, the mounting sinking can be recessed from the second surface 21b of the bearing 100 toward the direction of the cylinder assembly, so that the installation The height of the sinking groove is lower than the height of the outer peripheral reinforcing rib 42, in other words, the distance between the bottom wall of the sinking groove and the first surface 21a is smaller than that between the end surface of the outer peripheral reinforcing rib 42 away from the cylinder assembly and the first surface 21a At this time, the installation hole 5 is formed on the installation sinker, so that after the threaded fastener is assembled, the head of the threaded fastener can sink into the installation sinker, thereby improving the overall structure of the compression mechanism 1000 .

In this way, the bearing 100 can also be formed by casting, and then it can be machined on the surface of the mounting boss 44 or the surface of the sinking groove, thereby further reducing the machining area and reducing the weight of the bearing 100. Processing cost and processing time. In addition, since only the peripheral reinforcing rib 42, the mounting boss 44 or the sinking groove on the bearing 100 need to be machined, there is no need to leave sufficient machining allowance when casting the bearing 100, thereby further reducing the processing cost of the casting of the bearing 100 .

Here, it should be noted that the cross-sectional shape of the first rib 3 and the second rib 4 can be set according to actual requirements, so as to better meet the actual requirements, such as the shape of the first rib 3 and the second rib 4 The cross-sectional shape can be rectangular, triangular, trapezoidal, drum-shaped, etc., and the peripheral reinforcing rib 42 can be formed into a variable cross-sectional rib according to the design requirements of the mounting hole 5 . In addition, the projection shapes of the first rib 3 and the second rib 4 on the reference plane can also be designed according to actual requirements, so as to better meet actual requirements.

In some other embodiments of the present utility model, the compression mechanism 1000 can also include a muffler (not shown in the figure), and the muffler can be fixed on the side of the bearing 100 with the exhaust valve seat 6 away from the cylinder assembly, so as to reduce the The exhaust noise of the compressor, because some grooves are defined between the first rib 3 and the second rib 4, after the muffler and the bearing 100 are assembled in place, the noise reduction between the muffler and the bearing 100 can be improved. Space, so that the noise reduction effect can be effectively improved, and the silencer volume and frequency of the silencer can be improved.

The compressor according to the embodiment of the second aspect of the utility model includes the compression mechanism 1000 for a compressor according to the embodiment of the above first aspect of the utility model. Wherein, the compressor may be a vertical compressor or a horizontal compressor.

According to the compressor of the embodiment of the utility model, the overall performance of the compressor is improved by providing the compression mechanism 1000 for the compressor in the embodiment of the first aspect.

In describing the present invention, it should be understood that the terms "width", "thickness", "upper", "lower", "top", "bottom", "inner", "outer", "axial" The orientation or positional relationship indicated by , "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the utility model and simplifying the description, rather than indicating or implying the referred device Or elements must have a specific orientation, be constructed and operate in a specific orientation, and thus should not be construed as limiting the invention.

In addition, the terms "first" and "second" are used for descriptive purposes only, and cannot be interpreted as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features. Thus, a feature defined as "first" and "second" may explicitly or implicitly include one or more of these features. In the description of the present utility model, "plurality" means two or more, unless otherwise specifically defined.

In this utility model, unless otherwise specified and limited, terms such as "installation", "connection", "connection" and "fixation" should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection. Connected, or integrated; it can be directly connected or indirectly connected through an intermediary, and it can be the internal communication of two elements or the interaction relationship between two elements. Those of ordinary skill in the art can understand the specific meanings of the above terms in the present utility model according to specific situations.

In the present invention, unless otherwise clearly specified and limited, the first feature may be in direct contact with the first feature or the first feature and the second feature through an intermediary indirect contact. Moreover, "above", "above" and "above" the first feature on the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. "Below", "beneath" and "beneath" the first feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is less horizontally than the second feature.

In the description of this specification, descriptions referring to the terms "one embodiment", "some embodiments", "example", "specific examples", or "some examples" mean that specific features described in connection with the embodiment or example , structures, materials or features are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the described specific features, structures, materials or characteristics may be combined in any suitable manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine different embodiments or examples and features of different embodiments or examples described in this specification without conflicting with each other.

Although the embodiments of the present invention have been shown and described, those skilled in the art can understand that various changes, modifications, substitutions and modifications, the scope of the present invention is defined by the claims and their equivalents.

Claims (17)

1. A compression mechanism for a compressor, characterized in that it comprises: a cylinder assembly and a bearing arranged at one end of the cylinder assembly in the axial direction, the cylinder assembly includes a cylinder with a compression chamber inside the cylinder, and Bearings include: Journal; a flange portion, the flange portion is provided between the journal portion and the cylinder assembly, and in the axial direction of the cylinder assembly, the flange portion includes a support axially opposite to the cylinder assembly Department; and A plurality of first reinforcing ribs, each of the first reinforcing ribs extends along the inner and outer directions and is arranged on a side of the supporting part away from the cylinder assembly, and the plurality of first reinforcing ribs are on the supporting part The distribution is spaced apart in the circumferential direction. 2. The compression mechanism for a compressor according to claim 1, wherein a slide groove extending radially along the cylinder is formed on the cylinder, and one of the plurality of first reinforcing ribs The first reinforcing rib is arranged opposite to the slide slot in the radial direction of the cylinder. 3. The compression mechanism for a compressor according to claim 2, characterized in that the width of the first reinforcing rib disposed opposite to the sliding vane groove in the radial direction of the cylinder is larger than the width of the plurality of The width of each of the remaining first reinforcing ribs in the first reinforcing ribs. 4. The compression mechanism for a compressor according to claim 2, wherein a cavity is defined between every two adjacent first ribs, and the radial direction of the cylinder and the sliding plate The depth of the cavities on both sides of the first reinforcing rib opposite to the groove is smaller than the depth of the cavity defined between the remaining first reinforcing ribs in the plurality of first reinforcing ribs. 5. The compression mechanism for a compressor according to claim 1, wherein a suction hole communicating with the compression chamber is formed on the cylinder, and at least one of the plurality of first reinforcing ribs The first reinforcing rib is arranged corresponding to the suction hole in the axial direction of the cylinder. 6. The compression mechanism for a compressor according to claim 1, wherein the supporting portion has a discharge valve seat, and the two ends of the discharge valve seat in the length direction are provided with the first Ribs. 7. The compression mechanism for a compressor according to any one of claims 1-6, wherein the bearing further comprises: The second reinforcing rib is provided on a side of the supporting part away from the cylinder assembly and extends along the circumferential direction of the supporting part. 8. The compression mechanism for a compressor according to claim 7, wherein the second reinforcing rib comprises an inner peripheral reinforcing rib, and the inner peripheral reinforcing rib is connected between the shaft neck and the support between departments. 9 . The compression mechanism for a compressor according to claim 8 , characterized in that, along the direction from the inside to the outside, the axial thickness of the inner circumferential reinforcing rib gradually decreases. 10. The compression mechanism for a compressor according to claim 8, wherein the second reinforcing rib comprises a transitional reinforcing rib, and the transitional reinforcing rib is connected between the outer edge of the inner circumferential reinforcing rib and the between the inner ends of the first ribs. 11. The compression mechanism for a compressor according to claim 7, wherein the second reinforcing rib includes an outer peripheral reinforcing rib, and the outer peripheral reinforcing rib is arranged on the outer edge of the supporting part and the second reinforcing rib. between the outer ends of a stiffener. 12 . The compression mechanism for a compressor according to claim 11 , characterized in that, the outer peripheral reinforcing rib is formed with a through mounting hole. 13 . 13 . The compression mechanism for a compressor according to claim 12 , wherein, in the radial direction of the support portion, the installation holes are arranged corresponding to the first reinforcing ribs. 14 . 14. The compression mechanism for a compressor according to claim 12, characterized in that, in the axial direction of the cylinder assembly, the end face of the installation hole on the side away from the cylinder assembly is located at the first The side of the rib away from the cylinder assembly. 15. The compression mechanism for a compressor according to claim 12, wherein a mounting boss protruding away from the cylinder assembly is formed on the outer peripheral reinforcing rib, and the mounting hole is formed in the on the mounting boss described above. 16. The compression mechanism for a compressor according to claim 12, characterized in that, the outer peripheral reinforcing rib is formed with a mounting sinking recessed toward the direction of the cylinder assembly, and the mounting hole is formed in the Install on the sink. 17. A compressor, characterized by comprising the compression mechanism for a compressor according to any one of claims 1-16.