compressor

Abstract

The utility model provides a kind of compressor, including motor assembly, motor assembly includes motor rotor and motor stator, motor rotor includes rotor core and balance block, motor stator includes stator core, stator core has multiple stator teeth, form stator slot between adjacent two stator teeth, on the projection of any radial surface of rotor core, the central angle of circle formed by the slot center line of adjacent two stator slots is a, a≤24°, balance block includes the balance block ontology extending along the circumference of rotor core and windward end and leeward end, the cross-sectional area of windward end and / or leeward end is smaller and smaller along the direction of away from balance block ontology.The utility model can improve the drainage effect of the refrigerant airflow formed by balance block at stator slot to some extent, reduce the collision probability of this part of refrigerant airflow and the inner circumferential surface of stator tooth shoe, and then can alleviate the occurrence of operating noise and vortex phenomenon caused by this part of refrigerant airflow to some extent.

Description

Technical Field

[0001] This utility model belongs to the field of motor design technology, and specifically relates to a compressor. Background Technology

[0002] In existing technologies, to ensure the dynamic balance of the motor rotor assembly, balancing blocks are often installed at the ends of the rotor assembly. The windward or leeward end of these balancing blocks is designed as a planar structure (see...). Figure 1 As shown), when this motor rotor assembly is applied inside the compressor, it generates a fan-like action to draw refrigerant outward. A larger flow of refrigerant, under the action of the rotating counterweight, is drawn outward to the stator side of the motor and collides with the stator's solid portion (i.e., the inner wall of the stator gear shoe). This collision of refrigerant at the stator's solid portion contributes to the compressor's impact noise, worsening the overall operating noise level. Furthermore, it easily creates eddies in the collision area (such as...). Figure 2 and Figure 3 As shown in the figure, this leads to turbulent flow field inside the compressor, which is not conducive to reducing the compressor's oil discharge rate and power consumption, and further aggravates the compressor's operating noise. Utility Model Content

[0003] Therefore, this utility model provides a compressor that can overcome the technical problems in the related art where a large amount of refrigerant collides with the physical parts of the motor stator during the rotation of the balance block, resulting in deterioration of compressor operating noise and hindering the reduction of compressor oil discharge rate and power consumption.

[0004] To address the aforementioned problems, this utility model provides a compressor, including a motor assembly for driving a pump body assembly to generate compressed refrigerant. The motor assembly includes a motor rotor and a motor stator. The motor rotor includes a rotor core and a counterweight disposed on one end face of the rotor core. The motor stator includes a stator core with multiple stator teeth extending toward one side of the motor rotor. Each stator tooth is evenly spaced along the circumference of the rotor core, and a stator slot is formed between two adjacent stator teeth. Projected onto any radial surface of the rotor core, the central angle formed by the center lines of two adjacent stator slots is α, where α ≤ 24°. The counterweight includes a counterweight body extending along the circumference of the rotor core and two circumferential ends of the counterweight body: a windward end and a leeward end. The cross-sectional area of ​​the windward end and / or the leeward end decreases in the direction away from the counterweight body.

[0005] In some embodiments, a stator slot is formed between the tooth shoes of two adjacent stator teeth, the circumferential width of each stator slot is L, and the circumferential extension width of each tooth shoe is S, where 0.18≤L / S≤0.48.

[0006] In some embodiments, a circumferential gap is formed between the stator core and the radial outer wall of the balance block, and the radial thickness of the circumferential gap is d, where d ≥ 0.6 mm.

[0007] In some embodiments, the radially outer wall of the windward end gradually slopes toward the radially inner wall of the balance block body in a direction away from the balance block body.

[0008] In some embodiments, the radially inner wall of the windward end gradually slopes toward the radially outer wall of the balance block body in a direction away from the balance block body.

[0009] In some embodiments, the radially outer wall of the windward end gradually tilts towards the radially inner wall of the balance block body in a direction away from the balance block body, and the radially inner wall of the windward end gradually tilts towards the radially outer wall of the balance block body in a direction away from the balance block body.

[0010] In some embodiments, the radially outer wall of the windward end gradually slopes toward the radially inner wall of the balance block body in a direction away from the balance block body, and the axial thickness of the windward end gradually decreases in a direction away from the balance block body.

[0011] In some implementations, the windward end has a pointed structure.

[0012] The compressor provided by this utility model has the following beneficial effects:

[0013] By limiting the central angle α formed by the center lines of two adjacent stator slots to no more than 24°, the stator core has a relatively large number of slots (no less than fifteen slots). This reduces the span angle of the continuous solid wall portion of the stator core facing the motor rotor, thereby improving the flow of refrigerant airflow from the stator slots to the balance block. This reduces the probability of collision between this refrigerant airflow and the inner wall of the stator tooth shoe (i.e., the solid structure), thus mitigating the operating noise and eddy current phenomenon caused by this refrigerant airflow. Furthermore, the cross-sectional area of ​​the windward and / or leeward ends decreases along the direction away from the balance block body, enabling the windward end to guide the refrigerant during the balance block rotation. This reduces refrigerant resistance, compressor power consumption, and further reduces compressor operating noise. Attached Figure Description

[0014] To more clearly illustrate the embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings in the following description are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0015] Figure 1 This is a schematic diagram of the three-dimensional structure of a balance block in existing technology;

[0016] Figure 2 This is a schematic diagram of the state in which the balance block pump delivers refrigerant into the stator slot in the existing technology;

[0017] Figure 3 yes Figure 2 A schematic diagram showing the state of eddy currents generated when the motor rotor rotates at a certain angle and the refrigerant pumped by the balance block impacts the inner circular wall of the stator tooth shoe.

[0018] Figure 4 This is a schematic diagram of the internal structure of the compressor in an embodiment of the present invention (only the motor rotor and motor stator are shown, other components are omitted). The arrows in the figure indicate the refrigerant flow path.

[0019] Figure 5 This is a schematic diagram of the structure of the balance block in an embodiment of the present invention, where the arrows indicate the refrigerant flow path.

[0020] Figure 6 This is a schematic diagram of another structure of the balance block in an embodiment of the present invention. The arrows in the diagram indicate the refrigerant flow path.

[0021] Figure 7 This is another structural schematic diagram of the balance block in this utility model embodiment, where the arrows indicate the refrigerant flow path;

[0022] Figure 8 yes Figure 7 The top view shows the refrigerant flow path indicated by the arrows.

[0023] Figure 9 This is another structural schematic diagram of the balance block in an embodiment of the present utility model;

[0024] Figure 10 yes Figure 9 A schematic diagram of the three-dimensional structure of the balance block in the diagram;

[0025] Figure 11 yes Figure 10 Side view;

[0026] Figure 12 yes Figure 10 Top view;

[0027] Figure 13 This is an axial projection schematic diagram of the stator core in this utility model.

[0028] The attached figures are labeled as follows:

[0029] 11. Stator core; 111. Stator teeth; 112. Stator slots; 113. Tooth shoe; 12. Stator winding; 21. Rotor core; 22. Balance block; 221. Balance block body; 222. Windward end; 223. Leeward end. Detailed Implementation

[0030] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.

[0031] In the description of this utility model, it should be understood that the directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this utility model. The directional terms "inner" and "outer" refer to the inner and outer contours of each component itself.

[0032] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90° or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0033] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this utility model.

[0034] like Figure 1 As shown, in existing compressors, the balance block has a relatively large frontal area. During compressor operation, the balance block rotates with the motor rotor, creating a fan effect that drives the refrigerant to flow radially outward from the balance block. However, after leaving the balance block from its frontal end, the refrigerant encounters the stator. The stator, located near the balance block's end face, has slots and solid sections spaced apart in a circumferential direction. Specifically, in a conventional compressor... Figure 2 As shown, when the windward side of the balance weight is close to the stator slot gap (i.e., slot opening), the refrigerant can flow smoothly out of the motor from the gap; as Figure 3 As shown, when the windward surface of the balance block approaches the motor body (i.e., the inner circular wall of the stator tooth shoe), the refrigerant cannot flow out smoothly and can only collide with the body wall (i.e., the inner circular wall of the stator tooth shoe). If the refrigerant after the collision cannot flow out from the slot gap in time, it will generate additional noise. More seriously, it will generate eddies, which will disrupt the internal flow field of the compressor and cause a series of problems such as high oil discharge rate and high power consumption of the compressor.

[0035] Based on the aforementioned shortcomings of the existing technology, and in conjunction with [see also...] Figures 4 to 13 As shown, according to an embodiment of the present invention, a compressor is provided, including a motor assembly (not shown in the figure) for driving a pump body assembly (not shown in the figure) to generate compressed refrigerant. The motor assembly includes a motor rotor (not shown in the figure) and a motor stator (not shown in the figure). The motor rotor includes a rotor core 21 and a balance block 22 disposed on one end face of the rotor core 21. The motor stator includes a stator core 11, the stator core 11 having a plurality of stator teeth 111 extending toward one side of the motor rotor, and each stator tooth 111 being evenly spaced along the circumference of the rotor core 21. Furthermore, a stator winding 12 is wound around each stator tooth 111, and a stator slot 112 is formed between two adjacent stator teeth 111. When projected onto any radial surface of the rotor core 21, the central angle formed by the center lines of two adjacent stator slots 112 is α, where α ≤ 24°. The balance block 22 includes a balance block body 221 extending circumferentially along the rotor core 21, and a windward end 222 and a leeward end 223 located at both circumferential ends of the balance block body 221. The cross-sectional area of ​​the windward end 222 and / or the leeward end 223 decreases in the direction away from the balance block body 221.

[0036] In this technical solution, the central angle α formed by the center lines of two adjacent stator slots 112 is limited to no more than 24°, thereby making the number of stator slots 112 in the stator core 11 relatively large (no less than fifteen slots). This reduces the span angle of the continuous solid wall portion of the stator core 11 facing the motor rotor, thereby improving the flow of refrigerant airflow from the stator slots 112 to the balance block 22 and reducing the probability of collision between this refrigerant airflow and the inner circular wall (i.e., solid structure) of the stator teeth 111. This can alleviate the operating noise and eddy current phenomenon caused by this refrigerant airflow to a certain extent. The cross-sectional area of ​​the windward end 222 and / or the leeward end 223 decreases along the direction away from the balance block body 221, enabling the windward end 222 to guide the refrigerant during the rotation of the balance block 22, reducing the refrigerant resistance, reducing compressor power consumption, and further reducing compressor operating noise.

[0037] In some implementation methods, see details. Figure 13 As shown, stator slots are formed between the tooth shoes 113 of two adjacent stator teeth 111, the circumferential width of each stator slot is L, and the circumferential extension width of each tooth shoe 113 is S, 0.18≤L / S≤0.48.

[0038] In this technical solution, the ratio of L to S is further limited, which can ensure that the proportion of the slot is not too small while satisfying the reliable limiting of the stator winding 12, thereby ensuring the smooth flow of refrigerant air.

[0039] In some embodiments, a circumferential gap is formed between the stator core 11 and the radially outer wall of the balance block 22, the radial thickness of the circumferential gap being d, where d ≥ 0.6 mm. See details [link to relevant documentation]. Figure 4 As shown, the radius of the inner circle of the stator core 11 (that is, the inner circle wall of each toothed shoe 113) is R, and the radius of the radial outer wall of the balance block 22 is r, where Rr ≥ 0.6 mm.

[0040] In this technical solution, the minimum distance between the radial outer wall of the balance block 22 and the stator core 11 is limited. When the distance is not less than 0.6mm, even if some refrigerant is squeezed to circumferential movement by the windward end of the balance block 22, it can flow smoothly from the gap to the next stator slot 112 and then flow smoothly out of the motor, thus ensuring the smooth flow of refrigerant.

[0041] In some implementation methods, see details. Figure 4 As shown, the radially outer wall of the windward end 222 gradually tilts towards the radially inner wall of the balance block body 221 in the direction away from the balance block body 221.

[0042] In this technical solution, the windward end of the balance block 22 is provided with a flow guiding outer side. The flow guiding outer side gradually approaches the inner side of the balance block (that is, the inner wall of the balance block body 221 mentioned above) from the front end of the windward end 222. This setting changes the flow direction of the refrigerant pump, so that the angle between the refrigerant flow direction and the stator body part is reduced, thereby allowing the refrigerant to move at least partially along the circumferential direction, and then flow out of the stator core 11 in the next empty slot.

[0043] In some implementation methods, see details. Figure 5 As shown, the radial inner wall of the windward end 222 gradually tilts towards the radial outer wall of the balance block body 221 in the direction away from the balance block body 221.

[0044] In this technical solution, the windward end of the balance block 22 is provided with a flow guiding inner side, which gradually approaches the outer side of the balance block from the front end of the windward end. This arrangement will pump at least part of the refrigerant to the inner side of the rotor, thereby greatly reducing the amount of refrigerant pumped outward, thus reducing the collision caused by a large amount of refrigerant being transported to the stator core 11 side.

[0045] In some implementation methods, see details. Figure 6 As shown, the radial outer wall of the windward end 222 gradually tilts towards the radial inner wall of the balance block body 221 in the direction away from the balance block body 221, and the radial inner wall of the windward end 222 gradually tilts towards the radial outer wall of the balance block body 221 in the direction away from the balance block body 221.

[0046] In this technical solution, the balance block 22 is provided with both an inner and an outer guide surface. This reduces the flow rate of refrigerant pumped to the outside and reduces the windward angle of the outer guide surface, thereby mitigating the impact between the refrigerant and the stator body.

[0047] In some implementation methods, see details. Figure 7 and Figure 8 As shown, the radially outer wall of the windward end 222 gradually tilts towards the radially inner wall of the balance block body 221 in the direction away from the balance block body 221, and the axial thickness of the windward end 222 gradually decreases in the direction away from the balance block body 221.

[0048] In this technical solution, while the balance block 22 has a flow guiding surface (i.e., the outer flow guiding surface) formed by the radial outer wall, it also has a flow guiding upper surface, which diverts part of the refrigerant to the upper end of the balance block 22 (i.e., the side away from the rotor core 21), reducing the refrigerant flow rate that directly impacts the stator. At the same time, the flow guiding outer surface changes the flow direction of the refrigerant pump, reducing the angle between the refrigerant flow direction and the stator body, so that the refrigerant can at least partially move along the circumferential direction, and then flow out of the stator core 11 in the next stator slot 112, thereby greatly reducing the direct impact between the refrigerant and the stator.

[0049] In some embodiments, the windward end 222 has a pointed structure, see details below. Figures 9 to 12 As shown, the aforementioned sharp-angled structure can be a roughly conical structure, which allows the balance block 22 to have guide surfaces in the upward, downward, inward, and outward directions. The upward, downward, and inward guide surfaces divert most of the refrigerant, while the remaining refrigerant is guided to the outside and flows out through the stator slot 112. The outer guide surface gradually approaches the inner surface of the balance block from the front end of the windward end 222. This arrangement changes the flow direction of the refrigerant pump, reducing the angle between the refrigerant flow direction and the stator body, so that the refrigerant can at least partially move in the circumferential direction, and then flow out of the stator core 11 through the next stator slot 112.

[0050] It should be noted that, in order to improve the guidance of refrigerant airflow on each guide surface, the aforementioned tilt is preferably a smooth arc transition.

[0051] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0052] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model. The above description is only a preferred embodiment of this utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of this utility model, and these improvements and modifications should also be considered within the protection scope of this utility model.

Claims

1. A compressor, characterized in that, The system includes a motor assembly for driving the pump body assembly to generate compressed refrigerant. The motor assembly includes a motor rotor and a motor stator. The motor rotor includes a rotor core (21) and a counterweight (22) disposed on one end face of the rotor core (21). The motor stator includes a stator core (11) having a plurality of stator teeth (111) extending toward one side of the motor rotor. Each stator tooth (111) is evenly spaced along the circumference of the rotor core (21), and a stator slot is formed between two adjacent stator teeth (111). (112) Projected onto any radial surface of the rotor core (21), the central angle formed by the center lines of two adjacent stator slots (112) is a, a≤24°; the balance block (22) includes a balance block body (221) extending circumferentially along the rotor core (21) and windward end (222) and leeward end (223) at both circumferential ends of the balance block body (221), the cross-sectional area of ​​the windward end (222) and / or leeward end (223) becoming smaller and smaller along the direction away from the balance block body (221).

2. The compressor according to claim 1, characterized in that, A stator slot is formed between the tooth shoes (113) of two adjacent stator teeth (111), the circumferential width of each stator slot is L, and the circumferential extension width of each tooth shoe (113) is S, 0.18≤L / S≤0.

48.

3. The compressor according to claim 1 or 2, characterized in that, A circumferential gap is formed between the stator core (11) and the radial outer wall of the balance block (22), and the radial thickness of the circumferential gap is d, where d ≥ 0.6 mm.

4. The compressor according to claim 1, characterized in that, The radial outer wall of the windward end (222) gradually tilts towards the radial inner wall of the balance block body (221) in the direction away from the balance block body (221).

5. The compressor according to claim 1, characterized in that, The radial inner wall of the windward end (222) gradually tilts towards the radial outer wall of the balance block body (221) in the direction away from the balance block body (221).

6. The compressor according to claim 1, characterized in that, The radial outer wall of the windward end (222) gradually tilts towards the radial inner wall of the balance block body (221) in the direction away from the balance block body (221), and the radial inner wall of the windward end (222) gradually tilts towards the radial outer wall of the balance block body (221) in the direction away from the balance block body (221).

7. The compressor according to claim 1, characterized in that, The radial outer wall of the windward end (222) gradually tilts towards the radial inner wall of the balance block body (221) in the direction away from the balance block body (221), and the axial thickness of the windward end (222) gradually decreases in the direction away from the balance block body (221).

8. The compressor according to claim 1, characterized in that, The windward end (222) has a pointed structure.

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