Compressor

Abstract

The utility model discloses a compressor, relates to compressor technical field, compressor includes casing, drive motor and balance weight, balance weight includes main part, on the main part is provided with the recess that deviates the center of main part, the volume ratio of recess to balance weight is less than or equal to 2 / 3, makes the balance weight's gravity center deviates its geometric centre arrangement, and is equipped with the balance weight. The main body part is provided with a central through hole for the crankshaft to penetrate through and first through-flow holes located in the peripheral side of the central through hole and communicated with the second through-flow holes in the rotor, and due to the fact that the balance blocks are continuous and uniform in shape and surface area distribution, fluid can smoothly bypass the balance blocks; local flow velocity change and pressure fluctuation are reduced, so that the problem of disturbing a flow field is solved, wind resistance is reduced, meanwhile, loss of a gas-liquid mixture caused by disturbance can be reduced, the effect of improving the efficiency of the compressor is achieved, and the problems that an existing balance block easily damages the gas flow field, exhaust kinetic energy loss is increased, and the efficiency of the compressor is affected are solved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, and particularly relates to a compressor. Background Art

[0002] In a rotary compressor, a motor rotor is connected to a crankshaft to drive the crankshaft to rotate. Due to the influence of a rolling piston and gas force, there is a centrifugal force in the radial direction of the crankshaft during operation. Usually, balance weights are added on both end faces of the rotor to offset the centrifugal force.

[0003] Most of the existing balance weights are crescent-shaped and are installed at a position deviated from the center on the end face of the rotor. When the compressor is working, the motor rotor rotates at a high speed. At this time, the high-speed gas-liquid mixture discharged from the muffler will be disturbed by the balance weight when it reaches the through-hole of the rotor, damaging the gas flow field here, causing the gas to diverge around, affecting the return of the liquid refrigerant oil separated above to the oil sump, and further affecting the normal oil circuit circulation, as well as the lubrication and sealing effects of the compressor; the balance weight disturbs the flow field, increasing the flow resistance and the loss of exhaust kinetic energy, and affecting the efficiency of the compressor. Summary of the Utility Model

[0004] The main purpose of the utility model is to propose a compressor, aiming to solve the problems that the existing balance weight is easy to damage the gas flow field, increase the loss of exhaust kinetic energy, and affect the efficiency of the compressor.

[0005] To achieve the above purpose, the compressor proposed by the utility model includes:

[0006] A housing;

[0007] A driving motor, arranged in the housing, including a rotor, and a second through-hole is provided through the rotor; and,

[0008] A balance weight, the balance weight includes a main body portion, the main body portion has a first end face and a second end face arranged oppositely, the first end face is installed at the lower end of the rotor, a central through-hole for the crankshaft to pass through is provided on the main body portion, and a first through-hole located on the periphery of the central through-hole and communicated with the second through-hole is provided, and the first through-hole penetrates through the two end faces of the main body portion;

[0009] A groove is provided on the main body portion, the groove is arranged deviating from the center of the main body portion, the volume of the groove is V1, the volume of the balance weight is V, and V1≤2 / 3V.

[0010] In an embodiment, V1≤1 / 3V.

[0011] In an embodiment, the length of the groove in the circumferential direction of the main body portion is L1, the circumference of the main body portion is L, and L1≤1 / 2L.

[0012] In one embodiment, the groove depth of the groove is H1, the thickness of the balance weight is H, and H1 ≤ 1 / 2H.

[0013] In one embodiment, the groove depth of the groove is H1, the wall thickness of the bottom wall of the groove is t, and 2 mm ≤ t ≤ H1.

[0014] In one embodiment, the groove is recessed in the first end face of the main body portion.

[0015] In one embodiment, a plurality of the first flow holes are provided, and at least one of the first flow holes is provided at the bottom of the groove.

[0016] In one embodiment, the balance weight further includes an annular convex portion protruding from the second end face, and the annular convex portion is disposed around the periphery of the central through hole and the first flow hole.

[0017] In one embodiment, the outer peripheral surface of the annular convex portion is flush with the outer peripheral surface of the main body portion; or,

[0018] The outer diameter of the annular convex portion is smaller than the diameter of the main body portion.

[0019] In one embodiment, the height of the annular convex portion is h, and 1 mm ≤ h ≤ 20 mm; and / or,

[0020] The annular width of the annular convex portion is D, and 1 mm ≤ D ≤ 10 mm.

[0021] In one embodiment, the inner peripheral wall of the annular convex portion is tapered in a direction away from the main body portion.

[0022] In one embodiment, the main body portion and the annular convex portion are integrally formed; or,

[0023] The main body portion and the annular convex portion are detachably connected.

[0024] In one embodiment, the cross section of the first flow hole is circular, elliptical or polygonal.

[0025] In one embodiment, the main body portion further penetrates through a first connection hole for corresponding setting with a second connection hole on the rotor.

[0026] In one embodiment, an avoidance groove extending in the up and down direction is provided on the annular convex portion, and the avoidance groove penetrates through the annular convex portion;

[0027] The first connection hole corresponds to the avoidance groove.

[0028] In one embodiment, the compressor further includes a muffler located below the rotor assembly. An exhaust port communicating with the air outlet of the compression cylinder is provided at the top of the muffler, and the exhaust port is arranged facing the first through-flow hole.

[0029] The distance between the bottom of the balance weight and the top of the muffler is L, and the thickness of the balance weight is H, where H ≤ 1 / 2L.

[0030] In one embodiment, the cross-sectional area of the first through-flow hole is set to be greater than or equal to the cross-sectional area of the second through-flow hole; and / or,

[0031] The rotor is provided with a shaft hole for the crankshaft to pass through, and the area of the central through-hole is set to be greater than or equal to the area of the shaft hole.

[0032] In one embodiment, the compressor includes a carbon dioxide compressor.

[0033] In the technical solution of the present utility model, a balance weight is installed at the bottom of the rotor. The balance weight includes a main body portion, and a groove is provided on the main body portion. The groove is arranged offset from the center of the main body portion. The volume of the groove is V1, and the volume of the balance weight is V, where V1 ≤ 1 / 3V, so that the center of gravity of the balance weight deviates from its geometric center. During operation, the rolling piston and gas force can balance the centrifugal force existing radially on the crankshaft. A central through-hole for the crankshaft to pass through and a first through-flow hole located on the periphery of the central through-hole and communicating with the second through-flow hole on the rotor are provided on the main body portion. The first through-flow hole penetrates through both end faces of the main body portion. After the oil-gas mixture flows out through the first through-flow hole of the rotor, it will enter the second through-flow hole. The main body portion is symmetric about the central through-hole. When the rotor drives the balance weight to rotate, due to the continuous and uniform shape and surface area distribution of the balance weight, the fluid can smoothly bypass the balance weight, reducing local flow velocity changes and pressure fluctuations, thereby improving the problem of disturbed flow fields, reducing wind resistance, ensuring the oil circuit circulation inside the compressor, guaranteeing the lubricating oil required for the lubrication and sealing of the compressor, improving the reliability and service life of the compressor, and at the same time reducing the loss caused by the disturbance to the gas-liquid mixture, having the effect of improving the efficiency of the compressor, so as to solve the problem that the existing balance weight easily destroys the gas flow field, increases the exhaust kinetic energy loss, and affects the efficiency of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] In order to more clearly illustrate the technical solutions in the embodiments of the present utility model or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present utility model. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on the structures shown in these drawings.

[0035] Figure 1 It is a schematic cross-sectional view of a compressor in the related art;

[0036] Figure 2 is Figure 1 a schematic cross-sectional view of the rotor and the balance weight in

[0037] Figure 3 It is a schematic cross-sectional view of an embodiment of the compressor provided by the present invention;

[0038] Figure 4 is Figure 3 a schematic cross-sectional view of the rotor and the balance weight in

[0039] Figure 5 It is a schematic cross-sectional view of an embodiment of the balance weight provided by the present invention;

[0040] Figure 6 is Figure 3 a three-dimensional schematic view of the rotor in

[0041] Figure 7 It is a schematic structural view of an embodiment of the balance weight provided by the present invention;

[0042] Figure 8 is Figure 7 a schematic structural view of the balance weight from another perspective in

[0043] Explanation of the reference numerals in the drawings:

[0044] 100’, balance weight; 1’, rotor;

[0045] 100, balance weight; 11, main body part; 101, first end face; 102, second end face; 12, annular convex part; a, central through hole; b, first through-flow hole; c, groove; d, first connecting hole;

[0046] 200, driving motor; 1, rotor; e, second through-flow; f, shaft hole; k, second connecting hole;

[0047] 300, compressor; 2, housing; 3, silencer; g, exhaust port.

[0048] The realization, functional features and advantages of the object of the present invention will be further described with reference to the embodiments and the accompanying drawings. Detailed implementation manners

[0049] The following will clearly and completely describe the technical solutions in the embodiments of the present utility model in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without creative efforts belong to the scope of protection of the present utility model.

[0050] It should be noted that if there are directional indications (such as up, down, left, right, front, back...) involved in the embodiments of the present utility model, then such directional indications are only used to explain the relative positional relationship and movement conditions between components in a certain specific posture. If this specific posture changes, then the directional indications will also change accordingly.

[0051] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present utility model, then such descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In addition, if "and / or" or "and / or" appears throughout the text, its meaning includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, solution B, or a solution where A and B are satisfied simultaneously. In addition, the technical solutions between various embodiments can be combined with each other, but it must be based on the fact that those of ordinary skill in the art can implement it. When the combination of technical solutions results in contradictions or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present utility model.

[0052] In a rotary compressor, the motor rotor is connected to the crankshaft to drive the crankshaft to rotate. Due to the influence of the rolling piston and gas force, there is a centrifugal force in the radial direction of the crankshaft during operation. Usually, balance weights are added on both end faces of the rotor to offset the centrifugal force. Existing balance weights are mostly crescent-shaped and are installed at a position deviating from the center on the rotor end face. When the compressor is working, the motor rotor is rotating at a high speed. At this time, the high-speed gas-liquid mixture discharged from the muffler, when reaching the rotor flow hole, will be disturbed by the balance weight, destroying the gas flow field here, causing the gas to diverge in all directions, affecting the return of the liquid refrigerant oil separated above to the oil sump, thereby affecting the normal oil circuit circulation and also affecting the lubrication and sealing effects of the compressor; the balance weight disturbs the flow field, increasing the flow resistance and the loss of exhaust kinetic energy, affecting the compressor efficiency.

[0053] The present utility model proposes a compressor, aiming to solve the problems that the existing balance weight is prone to destroying the gas flow field, increasing the loss of exhaust kinetic energy, and affecting the compressor efficiency.

[0054] Please refer toFigures 3 to 6 In an embodiment of the present utility model, the compressor 300 includes a housing 2, a driving motor 200 and a balance weight 100. The driving motor 200 is disposed within the housing 2. The driving motor 200 includes a rotor 1 rotatably arranged along a rotation axis extending vertically. A second through-flow hole e is provided through the rotor 1. The center of gravity of the balance weight 100 is offset from its geometric center. The balance weight 100 includes a main body portion 11. The main body portion 11 has a first end face 101 and a second end face 102 which are oppositely arranged. The first end face 101 is mounted at the lower end of the rotor 1. A central through-hole a for the crankshaft to pass through and a first through-flow hole b located on the periphery of the central through-hole a and communicated with the second through-flow hole e are provided on the main body portion 11. The first through-flow hole b penetrates through the two end faces of the main body portion 11. A groove c is provided on the main body portion 11. The groove c is offset from the center of the main body portion 11. The volume of the groove c is V1, and the volume of the balance weight 100 is V, where V1 ≤ 2 / 3V.

[0055] It should be noted that, please refer to Figure 1 and Figure 2 In the related art, the balance weight 100' is in the shape of a crescent or composed of a single-sided balance + a reverse buckled disc, and is not symmetric about the rotation center of the rotor. The surface area of the crescent-shaped balance weight relative to the surrounding fluid is not evenly distributed during rotation, which will cause changes in local flow velocity and pressure fluctuations, thereby generating a disturbed flow field. This disturbance increases the hydrodynamic loss, reduces the efficiency, and causes additional noise and vibration.

[0056] At the same time, the high-pressure gas-liquid mixture is discharged from the muffler, passes through the through-flow hole on the rotor, and enters the upper space of the stator. Since the existing balance weight structure rotates at a high speed with the rotor, during this process, it will impact the gas-liquid mixture, changing its original path, causing some gas-liquid mixture to diverge in all directions, and destroying the internal flow and lubricating oil circulation path of the compressor.

[0057] It should also be noted that the normal lubricating oil circulation path: The lubricating oil in the oil sump enters the pump body compressor cavity from the oil supply hole at the bottom of the crankshaft to participate in the lubrication and sealing of the rotating components. Part of the lubricating oil will enter the compression cavity in the compression pump and be discharged through the muffler 3 along with the high-pressure gas. At this time, the gas-liquid mixture passes through the through-flow hole of the rotor 1 and enters the upper space of the stator assembly. The gas-liquid mixture in the upper space of the stator assembly is separated under the action of gravity separation, centrifugal separation, impact separation, etc., and the liquid oil droplets are separated. The separated lubricating oil flows back to the oil sump at the bottom of the compressor through the trimming gap reserved between the stator and the housing to participate in the subsequent oil supply, thus forming a complete lubricating oil circulation process inside the compressor.

[0058] It can be understood that since the groove c is arranged deviating from the center of the main body 11, the volume V1 of the groove c is set to be less than or equal to 2 / 3 times the volume of the balance weight 100, so that the mass on one side of the groove c is smaller, realizing the offset of the center of gravity of the balance weight 100.

[0059] It should be noted that the volume V of the balance weight 100 refers to the space occupied by the outer shape of the balance weight 100. When there are hollow structures such as holes and grooves inside the balance weight 100, the volume of the balance weight 100 includes the volume occupied by the hollow structures such as holes and grooves.

[0060] In the technical solution of the present utility model, a balance weight 100 is installed at the bottom of the rotor 1. The center of gravity of the balance weight 100 is arranged deviating from its geometric center, which can balance the centrifugal force existing in the radial direction of the crankshaft during the operation of the rolling piston and the gas force. The balance weight 100 includes a main body 11. A central through hole a for the crankshaft to pass through is provided on the main body 11, and a first through hole b located on the periphery of the central through hole a and corresponding to the second through hole e on the rotor 1 is provided. The first through hole b penetrates through the two end faces of the main body 11. After the oil-gas mixture flows out through the first through hole b of the rotor 1, it will enter the second through hole e. The main body 11 is symmetrical about the central through hole a. When the rotor 1 drives the balance weight 100 to rotate, due to the continuous and uniform shape and surface area distribution of the balance weight 100, the fluid can smoothly bypass the balance weight 100, reducing the local flow velocity change and pressure fluctuation, thereby improving the problem of the disturbed flow field, reducing the wind resistance, ensuring the oil circuit circulation inside the compressor 300, ensuring the lubricating oil required for the lubrication and sealing of the compressor 300, improving the reliability and service life of the compressor 300, and at the same time reducing the loss caused by the disturbance to the gas-liquid mixture, having the effect of improving the efficiency of the compressor 300, so as to solve the problem that the existing balance weight 100 is easy to damage the gas flow field, increasing the exhaust kinetic energy loss and affecting the efficiency of the compressor 300.

[0061] Further, in an embodiment, V1≤1 / 3V. The volume V1 of the groove c is set to be less than or equal to 1 / 3 times the volume of the balance weight 100, avoiding setting the groove c too large, so that the mass of the balance weight 100 itself is reduced too much, and it is difficult to achieve the purpose of significantly adjusting the center of gravity of the balance weight 100.

[0062] Of course, in addition to the form of restricting the volume of the groove c within the range of less than or equal to 1 / 3 times the volume of the balance weight 100 as described above, in this embodiment, the length of the groove c in the circumferential direction of the main body 11 is L1, and the circumference of the main body 11 is L, and L1≤1 / 2L. Similarly, it can also better realize the offset of the center of gravity and achieve a better counterweight purpose.

[0063] In this embodiment, the groove depth of the groove c is H1, and the thickness of the balance weight 100 is H, where H1 ≤ 1 / 2H. In this way, the offset of the center of gravity can be better achieved, and a better weight balancing purpose can be achieved.

[0064] Furthermore, the wall thickness of the bottom wall of the groove c is t, where 2 mm ≤ t ≤ H1. Setting the wall thickness of the bottom wall of the groove c to be greater than or equal to 2 mm enables the bottom of the groove c to have sufficient strength. At the same time, setting the wall thickness of the bottom wall of the groove c to be less than or equal to the groove depth of the groove c can better achieve the offset of the center of gravity and achieve a better weight balancing purpose.

[0065] Furthermore, in this embodiment, the groove c is recessed in the first end face 101 of the main body portion 11. Since the groove c faces away from the silencer 3, the bottom of the main body portion 11 is relatively flat, avoiding the balance weight 100 disturbing the flow field.

[0066] Furthermore, in this embodiment, a plurality of the first through holes b are provided, and at least one of the first through holes b is provided at the bottom of the groove c.

[0067] It should be noted that a plurality of the first through holes b need to be docked with a plurality of the second through holes e on the rotor 1. Then, the manufacturing precision of a plurality of the first through holes b and a plurality of the second through holes e needs to be strictly controlled to avoid misalignment between the two and an increase in flow resistance.

[0068] If the balance grooves avoid all of the first through holes b, each of the first through holes b needs to be accurately docked with the second through holes e on the rotor 1. By providing the groove c, the high-speed gas-liquid mixture located in the groove c and passing through the first through hole b can be transferred at the groove c, and the groove c can have a transfer function. In this way, regardless of whether the first through hole b at the bottom of the groove c can be accurately docked with the second through holes e on the rotor 1, the connection between them can be achieved through the balance groove.

[0069] It should be noted that the high-speed gas-liquid mixture discharged from the silencer 3 is sprayed towards the bottom of the balance weight 100. However, when the balance weight 100 rotates, the exhaust holes on the silencer 3 for discharging the high-speed gas-liquid mixture do not always align with the first through holes b. The high-speed gas-liquid mixture will impact on the bottom of the main body portion 11, causing a small part of the high-speed gas-liquid mixture to diverge around.

[0070] Of course, in addition to achieving the offset of the center of gravity by setting the groove c, the offset of the center of gravity can also be achieved by setting a counterweight hollow part, such as opening a through hole, or setting a larger aperture for some of the first flow holes b among the plurality of first flow holes b. Of course, the forms of achieving the offset of the center of gravity are not limited to the above examples. Those skilled in the art may make other changes under the inspiration of the technical essence of the embodiments of this specification. However, as long as the functions and effects achieved are the same or similar to those of the embodiments of this specification, they should all be covered within the protection scope of the embodiments of this specification.

[0071] Further, in order to make the high-speed gas-liquid mixture more concentrated, please refer to Figure 7 , in this embodiment, the balance weight 100 further includes an annular convex portion 12 protruding from the second end face 102, and the annular convex portion 12 is disposed around the center through hole a and the first flow hole b.

[0072] By setting the annular convex portion 12, the gas-liquid mixture can be guided to flow along a preset path, avoiding the disordered diffusion of the gas-liquid mixture, ensuring that most of the mixture can accurately pass through the first flow hole b instead of splashing everywhere or generating unnecessary turbulence. Moreover, the setting of the annular convex portion 12 can improve the efficiency of the gas-liquid mixture entering the flow hole, reduce the backflow of the gas-liquid mixture at the bottom of the rotor 1, reduce the hydrodynamic loss, and thus improve the overall efficiency of the compressor 300.

[0073] Further, in this embodiment, the outer peripheral surface of the annular convex portion 12 is set to be circular. In this way, the surface of the annular convex portion 12 provides a more uniform peripheral contour, and the influence of the annular convex portion 12 on the fluid during rotation is more consistent, and the fluid can bypass the balance weight 100 more smoothly.

[0074] Further, in one embodiment, the outer peripheral surface of the annular convex portion 12 is flush with the outer peripheral surface of the main body portion 11. In this way, the annular convex portion 12 can have a larger inner diameter and outer diameter, and can gather the high-speed gas-liquid mixture within the largest range.

[0075] In another embodiment, the outer diameter of the annular convex portion 12 is smaller than the diameter of the main body portion 11. In this way, the diameter of the annular convex portion 12 is smaller, and the material required for manufacturing the annular convex portion 12 is also less, which can reduce the cost to a certain extent.

[0076] Further, in this embodiment, the height of the annular convex portion 12 is h, 1 mm ≤ h ≤ 10 mm; and / or, the ring width of the annular convex portion 12 is D, 1 mm ≤ D ≤ 10 mm.

[0077] Preferably, the height of the annular convex portion 12 is set between 3 mm and 5 mm, which neither occupies too much space below the rotor 1 nor can play an aggregating role to reduce the backflow of the gas-liquid mixture at the bottom of the rotor 1.

[0078] The ring width of the annular convex portion 12 can be set uniformly or non-uniformly, that is, part is thinner and the other part is thicker. The inner peripheral wall of the annular convex portion 12 can be a circular circumference or can be set in a stepped shape. Of course, other possible shapes can also be used, which can be specifically determined according to the actual situation, and the embodiments of this specification do not limit this. Therefore, the ring width of the annular convex portion 12 is set within the range of 1 mm to 10 mm. Preferably, the ring width of the annular convex portion 12 is set between 2 mm and 5 mm.

[0079] Further, please refer to Figure 5 , in another embodiment, the inner peripheral wall of the annular convex portion 12 is set to be gradually expanded in the direction away from the main body portion 11. With such a setting, it is beneficial for demolding when the balance weight 100 is formed. Specifically, the included angle α formed between the inner peripheral wall of the annular convex portion 12 and the main body portion 11 satisfies 0° ≤ α ≤ 10°. Preferably, it is set between 3° and 5°.

[0080] In one embodiment, the main body portion 11 and the annular convex portion 12 are integrally formed. In this way, the balance weight 100 has higher structural strength and rigidity. Under high-speed rotation conditions, the overall stability of the balance weight 100 is better, and it is not easy to deform or be damaged. And it can ensure the precise geometric relationship between the main body portion 11 and the annular convex portion 12, avoiding the possible cumulative errors in the assembly process, reducing the maintenance workload and potential assembly errors, and reducing the production cost because the number of parts and assembly steps are reduced.

[0081] In another embodiment, the main body portion 11 and the annular convex portion 12 are detachably connected. The detachable design allows the replacement of the annular convex portion 12 with different specifications to adapt to different working conditions without replacing the entire balance weight 100, reducing the maintenance cost.

[0082] The way to achieve detachability can be to set a clamping structure, a screwing structure or an adhesive layer, etc. between the main body portion 11 and the annular convex portion 12. Of course, other possible connection forms can also be used, which can be specifically determined according to the actual situation, and the embodiments of this specification do not limit this.

[0083] Specifically, in this embodiment, the cross-section of the first flow-through hole b is set to be circular, elliptical or polygonal. The polygon can be square, trapezoidal or quasi-triangular, etc.

[0084] When a plurality of the first flow holes b are provided, the cross-sections of the respective first flow holes b among the plurality of first flow holes b may be set to the same shape. Of course, the cross-sections of some of the first flow holes b may be set to the same shape, and the cross-sections of the other part of the first flow holes b may be set to other shapes. It is also possible to adjust the shape and cross-sectional size of the first flow holes b so that the center of gravity of the balance weight 100 deviates from its geometric center.

[0085] Further, please refer to Figure 6 , to facilitate the fixing of the balance weight 100 to the rotor 1, the main body portion 11 is also provided with a first connection hole d for corresponding setting with a second connection hole k on the rotor 1. The balance weight 100 is connected by a connecting member passing through the first connection hole d and the second connection hole k.

[0086] The balance weight 100 and the rotor 1 may be fixed by means of bolt screwing, or may be fixed by means of riveting. Of course, other possible connection methods may also be adopted, and specifically, it may be determined according to the actual situation, and the embodiments of this specification do not limit this.

[0087] Specifically, in this embodiment, the annular convex portion 12 is provided with an avoidance groove j extending in the up and down direction, and the avoidance groove j penetrates through the annular convex portion 12; the first connection hole d is correspondingly arranged with the avoidance groove j. The avoidance groove j avoids interference between the annular convex portion 12 and the connecting member (such as a bolt) on the rotor 1, ensuring that the connecting member can smoothly pass through the first connection hole d and align and fix with the second connection hole h of the rotor 1, thereby realizing the reliable connection between the balance weight 100 and the rotor 1.

[0088] Specifically, in this embodiment, the compressor 300 further includes a silencer 3. The silencer 3 is located below the drive motor 200. The top of the silencer 3 is provided with an exhaust port g communicated with the air outlet of the compression cylinder, and the exhaust port g is arranged facing the first flow hole b. Thus, after the high-speed gas-liquid mixture discharged from the compression chamber is silenced by the silencer 3, it is discharged from the exhaust port g and sprayed toward the first flow hole b. Since the exhaust port g faces the inner periphery of the annular convex portion 12, the gas-liquid mixture flows along a preset path, avoiding the disorderly diffusion of the gas-liquid mixture, and ensuring that most of the mixture can accurately pass through the first flow hole b instead of splashing everywhere or generating unnecessary turbulence.

[0089] Specifically, in this embodiment, the distance between the bottom of the balance weight 100 and the top of the silencer 3 is L, and the thickness of the balance weight 100 is H, where H ≤ 1 / 2L.

[0090] Set the thickness of the balance weight 100 within the range of less than or equal to 1 / 2L. On the one hand, it can balance the centrifugal force and take cost into account at the same time. On the other hand, avoid setting the thickness of the balance weight 100 too thick, which will increase the resistance of fluid flow, cause turbulence and pressure loss, and then affect the efficiency and performance of the compressor 300. The high-speed ejected gas-liquid mixture may directly impact the bottom of the balance weight 100, causing strong mechanical shock and vibration. This will not only accelerate the wear of the balance weight 100, but also may have an adverse impact on the balance state of the rotor 1, increasing the vibration and noise of the rotor 1.

[0091] In this embodiment, the cross-sectional area of the first flow-through hole b is set to be greater than or equal to the cross-sectional area of the second flow-through hole e. In this way, when the oil-gas mixture rises, the oil-gas mixture passing through the second flow-through hole e is prevented from interfering with the bottom wall of the balance weight 100, and the oil-gas mixture in the second flow-through hole e can smoothly flow into the first flow-through hole b.

[0092] In this embodiment, the rotor 1 is provided with a shaft hole f for the crankshaft to pass through, and the area of the central through hole a is set to be greater than or equal to the area of the shaft hole f.

[0093] In this way, when the oil-gas mixture rises from the shaft hole f, it is prevented from interfering with the bottom wall of the balance weight 100, so that the oil-gas mixture in the shaft hole f can smoothly flow into the central through hole a.

[0094] Specifically, the compressor 300 includes a carbon dioxide compressor. A carbon dioxide compressor is a special compressor that uses carbon dioxide as the working medium and is usually used in a refrigeration system called "carbon dioxide transcritical cycle". It has no destructive effect on the ozone layer. In some application scenarios, the carbon dioxide system can achieve higher energy efficiency than traditional refrigeration systems.

[0095] The above is only an exemplary embodiment of the present invention, and does not limit the patent scope of the present invention. Any equivalent structural transformation made under the technical concept of the present invention by using the content of the specification and drawings of the present invention, or directly / indirectly applied in other related technical fields, is included in the patent protection scope of the present invention.

Claims

1. A compressor, characterized in that, Comprising: A housing; A drive motor, disposed within the housing, including a rotor, and a second through-flow hole is provided through the rotor; And, A balance weight, the balance weight including a main body portion having a first end face and a second end face disposed opposite to each other, the first end face being mounted at the lower end of the rotor, a central through-hole for the crankshaft to pass through is provided on the main body portion, and a first through-flow hole located on the periphery of the central through-hole and communicated with the second through-flow hole is provided, and the first through-flow hole penetrates through the two end faces of the main body portion; A groove is provided on the main body portion, the groove is offset from the center of the main body portion, the volume of the groove is V1, the volume of the balance weight is V, and V1 ≤ 2 / 3V.

2. The compressor according to claim 1, characterized in that, V1 ≤ 1 / 3V.

3. The compressor according to claim 1, characterized in that, The length of the groove in the circumferential direction of the main body portion is L1, the circumference of the main body portion is L, and L1 ≤ 1 / 2L.

4. The compressor according to claim 1, characterized in that, The depth of the groove is H1, the thickness of the balance weight is H, and H1 ≤ 1 / 2H.

5. The compressor according to claim 1, characterized in that, The depth of the groove is H1, the wall thickness of the bottom wall of the groove is t, and 2 mm ≤ t ≤ H1.

6. The compressor according to claim 1, wherein The groove is recessed in the first end face of the main body portion.

7. The compressor according to claim 1, characterized in that, A plurality of the first through-flow holes are provided, and at least one of the first through-flow holes is provided at the bottom of the groove.

8. The compressor according to claim 1, characterized in that, The balance weight further includes an annular convex portion protruding from the second end face, and the annular convex portion is disposed around the periphery of the central through-hole and the first through-flow hole.

9. The compressor according to claim 8, characterized in that, The outer peripheral surface of the annular convex portion is flush with the outer peripheral surface of the main body portion; or, The outer diameter of the annular convex portion is smaller than the diameter of the main body portion.

10. The compressor according to claim 8, wherein, The height of the annular convex portion is h, and 1 mm ≤ h ≤ 10 mm; and / or, The ring width of the annular convex portion is D, and 1 mm ≤ D ≤ 10 mm.

11. The compressor according to claim 8, characterized in that, The inner peripheral wall of the annular convex portion is tapered in a direction away from the main body portion.

12. The compressor according to claim 8, wherein, The main body portion and the annular convex portion are integrally formed; or, The main body portion and the annular convex portion are detachably connected.

13. The compressor according to claim 1, wherein, The cross-section of the first through-flow hole is circular, elliptical or polygonal.

14. The compressor according to claim 1, characterized in that, The main body portion is further provided with a first connection hole corresponding to a second connection hole on the rotor.

15. The compressor according to claim 14, characterized in that, An avoidance groove extending in the up-down direction is provided on the annular convex portion, and the avoidance groove penetrates through the annular convex portion; The first connection hole corresponds to the avoidance groove.

16. The compressor according to claim 1, characterized in that The compressor further includes a muffler located below the drive motor, and an exhaust port communicated with the air outlet of the compression cylinder is provided at the top of the muffler, and the exhaust port faces the first through-flow hole; The distance between the bottom of the balance weight and the top of the muffler is L, the thickness of the balance weight is H, and H ≤ 1 / 2L.

17. The compressor according to claim 1, wherein, The cross-sectional area of the first through-flow hole is set to be greater than or equal to the cross-sectional area of the second through-flow hole; and / or, The rotor is provided with a shaft hole for the crankshaft to pass through, and the area of the central through-hole is set to be greater than or equal to the area of the shaft hole.

18. The compressor according to any one of claims 1 to 17, characterized in that, The compressor includes a carbon dioxide compressor.

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