Scroll compressor with balance weight block
By introducing a balancing weight into the oil supply channel of the scroll compressor and actively supplying lubricant using centrifugal pressure, the problem of insufficient lubrication of the scroll compressor during low-speed rotation is solved, the lubrication effect of the thrust surface is improved, and wear and failure are prevented.
Patent Information
- Application Number
- CN202422906517.9
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-27
- Publication Date
- 2025-10-21
- Estimated Expiration
- 2034-11-27
AI Technical Summary
When the existing scroll compressor rotates at low speed, it cannot provide sufficient stirring force, resulting in insufficient lubrication of the thrust surface between the movable scroll component and the main bearing seat, causing excessive wear and failure of the kinematic pair.
A balancing weight with an oil supply channel is provided in the scroll compressor, and the centrifugal pressure generated by the rotating component is used to actively supply lubricant to the thrust surface between the movable scroll component and the main bearing seat.
Without changing the existing structure, active lubrication of the thrust surface between the movable scroll component and the main bearing seat is achieved, which solves the problem of insufficient lubrication and reduces wear and failure of the moving pair.
Smart Images
Figure CN223459551U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model discloses a scroll compressor with counterweight, and relates to the technical field of scroll compressors, in particular to a scroll compressor with counterweight. BACKGROUND
[0002] Scroll compressors are variable displacement compressors. Scroll compressors include a fixed scroll member having involute vanes and an orbiting scroll member having involute vanes that cooperate with the fixed scroll member. The vanes of the fixed scroll member and the orbiting scroll member intermesh to form a plurality of cavities of variable volume, thereby compressing a working fluid (e.g., a refrigerant or other gas). Typically, the working fluid is introduced into the variable cavities from a suction port, and the orbiting scroll member is caused to orbit with respect to the fixed scroll member by an eccentric member driven by a motor or other power input to effect compression of the working fluid. During operation of the scroll compressor, centrifugal forces or centrifugal moments generated by the eccentric member can cause vibration and noise in the compressor. Typically, a counterweight is provided at the upper end of the drive shaft of the rotating member to provide a counteracting centrifugal force or moment to balance the unbalance of the eccentric member. In addition, the orbiting scroll member is supported by a main bearing seat and a thrust plate during operation to provide axial constraint. Since the orbiting scroll member orbits with respect to the main bearing seat and the thrust plate, the thrust surface between the orbiting scroll member and the main bearing seat and the thrust plate needs to be sufficiently lubricated to reduce additional power loss and to avoid failure of the moving structure due to poor lubrication.
[0003] Taking a vertical scroll compressor as an example, the existing structure basically stores lubricating oil at the bottom of the internal cavity of the compressor. During operation of the compressor, the lubricating oil is upwardly fed to the eccentric hole in the upper end surface of the drive shaft under the centrifugal force or the pressure provided by the oil pump to achieve lubrication between the orbiting scroll bearing and the drive shaft. Meanwhile, the lubricating oil is fed to the main bearing through the horizontal channel provided in the main bearing portion of the drive shaft to achieve lubrication between the main bearing and the drive shaft. The two parts of lubricating oil are collected in the cavity between the main bearing seat and the orbiting scroll. The lubricating oil collected in the cavity is splashed to the lower surface of the end plate of the orbiting scroll due to the high-speed rotation of the counterweight, thereby achieving lubrication of the thrust surface between the main bearing seat and the orbiting scroll member as the orbiting scroll member orbits. Since the area is basically large at the bottom and tapered at the top, the space is relatively large, and the amount of effective lubricating oil entering the thrust surface is often small and unstable when the lubrication is achieved by splashing of the counterweight, especially in the case of low-speed rotation of the compressor. The lubricating oil cannot provide sufficient stirring force, which leads to insufficient lubrication of the thrust surface between the orbiting scroll member and the main bearing seat, resulting in excessive wear and even failure of the moving pair.
[0004] In view of the problems in the prior art, it is necessary to design a new scroll compressor with a balance weight to overcome the problems in the prior art. SUMMARY
[0005] According to the prior art, in the case of low-speed rotation of the compressor, the lubricant cannot be provided with sufficient stirring force, resulting in insufficient lubrication of the thrust surface between the orbiting scroll member and the main bearing seat, leading to excessive wear and even failure of the pair.
[0006] The technical means adopted by the utility model are as follows:
[0007] A scroll compressor with a balance weight, the scroll compressor comprising: a fixed scroll member, an orbiting scroll member, a balance weight, a drive shaft member, a main bearing seat and a main bearing seat thrust base plate; the drive shaft member is assembled in the main bearing seat and is radially constrained by the main bearing seat; the orbiting scroll member is assembled on the eccentric part of the drive shaft member and is axially constrained by the main bearing seat thrust base plate (1510); the orbiting scroll member is assembled in cooperation with the fixed scroll member; the main bearing seat thrust base plate is arranged on the upper part of the main bearing seat, and the top end thereof is in contact with the orbiting scroll base plate thrust surface of the orbiting scroll member; the fixed scroll member, the main bearing seat thrust base plate and the main bearing seat are fixedly connected by bolts or other means; the balance weight is arranged on the drive shaft member, and at least part or all of the balance weight is arranged in the main bearing cavity between the orbiting scroll disc base plate of the orbiting scroll member and the main bearing seat, the balance weight is in close cooperation with the drive shaft member and rotates together with the drive shaft member;
[0008] Further, the balance weight (1300) of the scroll compressor with a balance weight is further provided with an oil supply channel inside;
[0009] Further, the oil supply channel is formed by the balance weight annular channel and the upward channel on the balance weight, and the transverse channel, the eccentric channel and the annular channel on the drive shaft member, or a combination of several of them.
[0010] Further, the main body of the balance weight is an annular structure integrally machined with the eccentric mass part and the balance weight mounting part;
[0011] Further, a groove type balance weight annular channel is arranged on the inner side wall of the balance weight mounting part, and the balance weight and the drive shaft member form a closed annular channel after close cooperation;
[0012] Further, the eccentric mass part is provided with a balance weight protruding part;
[0013] Further, the balance weight protruding part is provided with an upward channel;
[0014] Further, the bottom end of the upward channel communicates with the annular channel of the balance weight, and the top end of the upward channel is open at the gap between the top end of the protruding portion of the balance weight and the orbiting scroll member.
[0015] Further, the annular channel of the balance weight is arranged eccentrically / concentrically.
[0016] Further, the annular channel of the balance weight is arranged eccentrically, and the center of the annular channel is offset from the rotation center of the balance weight by a distance e.
[0017] Further, the eccentric mass portion and the protruding portion of the balance weight are arranged in one of an integrated structure and a split structure.
[0018] Further, the upward channel of the protruding portion of the balance weight is arranged obliquely.
[0019] Further, a transverse channel is arranged at a position corresponding to the balance weight mounting portion of the drive shaft member.
[0020] Further, one end of the transverse channel communicates with the eccentric channel in the middle of the drive shaft member as a main oil supply, and the other end of the transverse channel corresponds to the annular channel of the balance weight.
[0021] Further, an annular channel is arranged at a position corresponding to the balance weight mounting portion of the drive shaft member.
[0022] Further, the annular channel of the drive shaft member communicates with the transverse channel.
[0023] It should be noted that since the driving force of the active oil supply mode in the utility model is derived from the centrifugal pressure generated by the rotating fluid, the relationship between the rotation speed of the rotating fluid, the rotation radius of the rotating fluid and the limit height of the vertically lifted fluid can be calculated. As shown in the following formula, p1 is the pressure generated at point p due to the rotation of the liquid; p2 is the pressure generated at point p due to the vertical height difference (only considering the centrifugal pressure generated due to the rotation of the liquid). Then, the following formula can be obtained: Figure 9
[0024]
[0025]
[0026] Wherein:
[0027] ρ is the density of the fluid (kg / m 3 )
[0028] ω is the rotation angular velocity of the fluid (rad / s)
[0029] r is the rotation radius of the fluid at this point (m)
[0030] g is the acceleration of gravity (m / s 2 )
[0031] h is the height of the fluid (m)
[0032] The centrifugal pressure generated by rotation can effectively improve the limit condition of the liquid to p1=p1 (without considering the pressure loss of other liquid flow). Therefore, the relationship of ω, r, h can be obtained as:
[0033]
[0034] According to r=30mm; ω=94.2rad / s (15Hz) calculation can obtain h=400mm, the h size in the drawing is far less than 400mm. Therefore, the centrifugal pressure generated by the rotation of the lubricating oil can effectively supply oil to the friction surface at a high position even at low speed (20Hz).
[0035] Compared with the prior art, the utility model has the following advantages:
[0036] 1. The scroll compressor with the balance weight block provided by the utility model realizes the active supply of lubricant to the thrust surface between the moving scroll component and the main bearing seat by using the centrifugal pressure generated by the rotating component.
[0037] 2. The scroll compressor with the balance weight block provided by the utility model provides a mode of actively supplying lubricant to the thrust surface between the moving scroll component and the main bearing seat without changing the existing scroll compressor main body structure.
[0038] In summary, the technical scheme of the utility model solves the problems in the prior art, such as the inability to provide sufficient stirring force for the lubricant during the operation of the scroll compressor, especially under low speed rotation, the insufficient lubrication of the thrust surface between the moving scroll component and the main bearing seat, the excessive wear, and the failure of the moving pair. DRAWINGS
[0039] In order to more clearly illustrate the technical scheme in the embodiments of the utility model or the prior art, the drawings needed in the embodiment or the prior art description will be briefly introduced below. Obviously, the drawings in the following description are some embodiments of the utility model, and those skilled in the art can also obtain other drawings according to these drawings without creative labor.
[0040] Figure 1 It is a structural schematic diagram of the utility model;
[0041] Figure 2 It is a balance weight block structural schematic diagram of the utility model;
[0042] Figure 3 Structure diagram of eccentric structure of annular passage of balance weight ring of the utility model;
[0043] Figure 4 Structure diagram of split structure of eccentric mass part and balance weight ring of the utility model;
[0044] Figure 5 Structure diagram of inclined design of upward passage of the utility model;
[0045] Figure 6 Structure diagram of eccentric mass part of the utility model is the structure diagram of balance weight ring;
[0046] Figure 7 Structure diagram of annular passage of the utility model is not set to drive shaft part;
[0047] Figure 8 Structure diagram of annular passage of the utility model is set to drive shaft part;
[0048] Figure 9 Formula of the utility model;
[0049] Figure 10 Local longitudinal section view of prior vertical scroll type compressor;
[0050] Figure 11 Top view of main bearing support seat part of prior scroll type compressor;
[0051] Figure 12 Structure diagram of balance weight ring of prior scroll type compressor.
[0052] In the drawing: 1000, scroll compressor 1100, fixed scroll part 1200, movable scroll part 1210, movable scroll thrust plate 1211, movable scroll base plate thrust surface 1300, balance weight ring 1310, balance weight ring protruding part 1320, balance weight ring annular passage 1330, upward passage 1340, balance weight ring mounting part 1350, eccentric mass part 1400, drive shaft part 1410, transverse passage 1420, eccentric passage 1430, eccentric part 1440, annular passage 1500, main bearing seat 1510, thrust base plate 1511, main driven bearing seat base plate thrust surface 1520, cavity DETAILED DESCRIPTION
[0053] It should be noted that the embodiments in the utility model and the features in the embodiments can be combined with each other without conflict. The utility model will be described in detail below with reference to the drawings and in combination with embodiments.
[0054] In order to make the purpose, technical scheme and advantages of the embodiments of the present application clearer, the technical scheme of the embodiments of the present application will be described clearly and completely below in combination with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is merely illustrative, and is by no means as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative labor fall within the scope of the present application.
[0055] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit exemplary embodiments according to the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, components, and / or groups thereof, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.
[0056] The relative arrangement of components and steps, numerical expressions, and numerical values set forth in the embodiments are not intended to limit the scope of the present application unless specifically stated otherwise. It should be clear that the sizes of the various portions shown in the drawings are not drawn to scale for ease of description. Techniques, methods, and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered as part of the authorized description where appropriate. In all examples shown and discussed herein, any specific values should be interpreted as merely exemplary, and not as limiting. Thus, other examples of exemplary embodiments can have different values. It should be noted that like reference numerals and letters refer to like items in the following drawings, and thus, once an item is defined in one drawing, it need not be discussed further in subsequent drawings.
[0057] In the description of the present application, it should be understood that the orientation words such as "front, rear, upper, lower, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" and the like indicate the orientation or positional relationship shown in the drawings, which is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the indicated device or element must have a particular orientation or be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the scope of protection of the present application: the orientation words "inner, outer" refer to the inner and outer relative to the contour of each component.
[0058] For ease of description, spatially relative terms such as "above," "above," "on the upper surface of," and "above" may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is inverted, a device described as "above" or "on top of" another device or structure would then be positioned as "below" or "below" the other device or structure. Thus, the exemplary term "above" may include both the orientations of "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used herein should be interpreted accordingly.
[0059] In addition, it should be noted that the use of words such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above words have no special meaning and therefore cannot be understood as limiting the scope of protection of this utility model.
[0060] Example 1
[0061] like Figure 1 As shown, the present invention provides a scroll compressor with a balancing weight, comprising a fixed scroll component 1100 with involute blades and an orbiting scroll component 1200 with involute blades that cooperates with the fixed scroll component. The eccentric portion 1430 of the drive shaft component 1400, driven by an electric motor or other power input, drives the orbiting scroll component 1200 to rotate relative to the fixed scroll component 1100 in a translational manner to achieve compression of the working fluid (during operation, the orbiting scroll 1200 does not rotate about its own axis). The drive shaft 1400 is radially constrained by the main bearing seat 1500. During operation, the orbiting scroll component 1200 is supported by the main bearing seat 1500 and the thrust plate 1510 to provide axial constraint. The main bearing seat 1500 and the thrust plate 1510 can be separate components or integrated components. Since the movable scroll component 1200 rotates linearly relative to the main bearing seat thrust plate 1510, strong sliding friction is generated between the movable scroll plate thrust surface 1211 and the active bearing seat plate thrust surface 1511, so sufficient lubrication must be provided between the movable scroll plate thrust surface 1211 and the active bearing seat plate thrust surface 1511 to reduce additional power loss and avoid failure of the kinematic pair function due to poor lubrication.
[0062] During the operation of the scroll compressor, the centrifugal force or centrifugal moment generated by the rotation of the eccentric component can cause vibration and noise of the compressor. A balance weight 1300 is arranged at the upper end of the rotating component driving shaft 1400 to provide a reverse centrifugal force or centrifugal moment to balance the unbalance amount generated by the eccentric component.
[0063] As shown in Figure 2 , the balance weight 1300 is composed of an eccentric mass portion 1350 in a substantially semicircular arc shape and a mounting portion 1350 in a circular ring shape.
[0064] As shown in Figure 1 , the balance weight 1300 is mounted on the eccentric driving shaft 1400 and located in the cavity 1520 between the main bearing seat 1500 and the dynamic scroll thrust plate 1210.
[0065] As shown in Figure 1 , during the operation of the scroll compressor, the lubricating oil at the bottom of the scroll compressor 1000 is upwardly supplied through the eccentric passage 1420 inside the driving shaft 1400 under the action of the centrifugal force or the pressure provided by the oil pump, flows through the eccentric hole on the upper end surface of the driving shaft 1400 to realize the lubrication between the dynamic scroll bearing and the eccentric portion of the driving shaft; at the same time, part of the lubricating oil in the eccentric passage 1420 of the driving shaft 1400 is supplied to the annular passage 1320 of the balance weight under the action of the oil pump pressure or the centrifugal pressure through the transverse passage 1410 of the driving shaft; further, under the action of the centrifugal pressure, the lubricating oil in the annular passage 1320 of the balance weight is supplied to the upward passage 1330 inside the protruding portion 1310 of the balance weight which is in communication with the annular passage 1320 of the balance weight under the action of the centrifugal pressure and is thrown out at the end thereof. The upward passage 1330 of the balance weight which is in communication with the annular passage 1320 of the balance weight is directly opened to the suitable height of the dynamic scroll base plate thrust surface 1211 and the main dynamic bearing seat base plate thrust surface 1511, and the lubricating oil thrown out at the end of the upward passage 1330 of the balance weight enters between the dynamic scroll base plate thrust surface 1211 and the main dynamic bearing seat base plate thrust surface 1511 during the translational rotation of the dynamic scroll component 1200, thereby completing the active lubrication thereof.
[0066] Embodiment 2
[0067] As shown in Figure 3 , (on the basis of embodiment 1, ) the utility model also provides a scroll compressor with a balance weight, the annular passage 1320 is eccentrically arranged, wherein the center of the annular passage 1320 is offset from the rotation center of the balance weight 1300 by a distance e. The advantage of this scheme is that the offset distance e increases the rotational radius of the lubricating oil, thereby increasing the centrifugal force of the lubricating oil during rotation, thereby increasing the upward oil supply pressure of the lubricating oil and improving the upward oil supply effect of the lubricating oil.
[0068] Example 3
[0069] like Figure 4 As shown, (based on Example 1), the present invention further provides a scroll compressor with a balancing weight. The balancing weight protrusion 1310 and its internal upward channel 1330 are designed separately from the balancing weight body 1300, and the two can be connected by interference fit, threads, etc. The advantage of this separate design is that it provides an optional and flexible installation solution, allowing the present invention to be applied without major modifications to existing solutions.
[0070] Example 4
[0071] like Figure 5 As shown, (based on Example 1), the present invention also provides a scroll compressor with a balancing weight, wherein the internal portion of the raised portion 1310 of the balancing weight 1300 is tilted toward the upward passage 1330. In this embodiment, the tilt angle and direction of the upward passage 1330 are aligned with the rotational direction of the scroll compressor, thereby improving the upward flow of lubricating oil.
[0072] Example 5
[0073] like Figure 6 As shown, (based on Example 1), the present invention further provides a scroll compressor with a balancing weight, wherein the eccentric mass 1350 of the balancing weight 1300 is integrated with the convex portion 1310. In this application, if space permits, the eccentric mass 1350 of the balancing weight 1300 is integrated with the convex portion 1310, that is, the eccentric mass 1350 is the convex portion 1310 itself.
[0074] Example 6
[0075] like Figure 7 As shown, (based on Example 1,) the present invention also provides a scroll compressor with a balancing weight block, wherein an annular channel (1440) is provided at a portion where the drive shaft component (1400) cooperates with the balancing weight block mounting portion (1340); the annular channel (1440) is communicated with the transverse channel (1410).
[0076] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the above embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present invention.
Claims
1. A scroll compressor having a counterbalancing weight, the scroll compressor (1000) comprising: The scroll compressor with the balance weight is characterized in that: The balance weight (1300) is internally provided with an oil supply channel; The oil supply channel is formed by the balance weight annular channel (1320) and the upward channel (1330) on the balance weight (1300), and the transverse channel (1410), the eccentric channel (1420) and the annular channel (1440) on the driving shaft component (1400), or several combinations thereof.
2. The scroll compressor with the balance weight according to claim 1 is characterized in that: The main body of the balance weight (1300) is an annular structure integrally processed with the eccentric mass portion (1350) and the balance weight mounting portion (1340); The inner side wall of the balance weight mounting portion (1340) is provided with a balance weight annular channel (1320) in the form of a groove, and the balance weight (1300) is tightly fitted with the driving shaft component (1400); The eccentric mass portion (1350) is provided with a balance weight protruding portion (1310); The balance weight protruding portion (1310) is provided with an upward channel (1330); The bottom end of the upward channel (1330) is communicated with the balance weight annular channel (1320), and the top is opened at the gap between the top end of the balance weight protruding portion (1310) and the scroll base thrust surface (1211) of the scroll component (1200).
3. The scroll compressor with the balance weight according to claim 2 is characterized in that: The balance weight annular channel (1320) is arranged eccentrically / concentrically. The eccentric arrangement of the annular passage (1320) of the balance weight is eccentric to the center of rotation of the balance weight (1300) by a distance e.
4. The scroll compressor with a balance weight according to claim 2, characterized in that: The eccentric mass (1350) and the balance weight protrusion (1310) are one of an integral structure and a split structure.
5. The scroll compressor with a balance weight according to claim 2, characterized in that: The upward passage (1330) of the balance weight protrusion (1310) is arranged obliquely.
6. The scroll compressor with a balance weight according to claim 1, characterized in that: The driving shaft component (1400) is provided with a transverse passage (1410) at a position corresponding to the balance weight mounting portion; One end of the transverse passage (1410) communicates with the eccentric passage (1420) in the middle of the driving shaft component (1400) as a main oil supply, and the other end corresponds to the annular passage (1320) of the balance weight.
7. The scroll compressor with a balance weight according to claim 1, characterized in that: The driving shaft component (1400) is provided with an annular passage (1440) at a position corresponding to the balance weight mounting portion (1340); The annular passage (1440) communicates with the transverse passage (1410).