WO2021196543A1

WO2021196543A1 - Scroll compressor

Info

Publication number: WO2021196543A1
Application number: PCT/CN2020/118304
Authority: WO
Inventors: 黄幼玲; 杨东辉
Original assignee: 艾默生环境优化技术(苏州)有限公司
Priority date: 2020-04-02
Filing date: 2020-09-28
Publication date: 2021-10-07

Abstract

A scroll compressor (1), comprising: a compressor mechanism (CM), the compressor mechanism (CM) comprising a fixed scroll (22) and a moving scroll (24). The moving scroll (24) comprises a drive linking part; a drive shaft (16), the drive shaft (16) comprising a shaft end face (62) and a driving part extending out from the shaft end face (62); and an eccentric bushing (11), the eccentric bushing being arranged between the drive linking part and the drive part, and comprising a bushing end face (21) facing towards the shaft end face (62). The bushing end face (21) comprises a first shape-cooperation part, and the shaft end face (62) comprises a second shape-cooperation part, the first shape-cooperation part and the second shape-cooperation part cooperating so as to limit the range of angles of eccentric rotation of the bushing (11) relative to the drive shaft (16). In the described scroll compressor (1) accurate mounting of an eccentric bushing (11) can be ensured, and the angle of eccentric rotation of the eccentric bushing relative to a drive shaft (16) can be limited to within an appropriate range.

Description

Scroll compressor

This application claims the priority of the following Chinese patent applications: a Chinese patent application filed with the Chinese Patent Office on April 2, 2020, with the application number 202010255362.0 and the invention titled "Scroll Compressor"; on April 2, 2020 The application number submitted to the Chinese Patent Office is 202020471199.7 and the Chinese patent application named "scroll compressor". The entire contents of these patent applications are incorporated into this application by reference.

Technical field

The present disclosure relates to a scroll compressor.

Background technique

This section provides background information related to the present disclosure, which does not necessarily constitute prior art.

Scroll compressors can be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems. The scroll compressor includes a compression mechanism for compressing working fluid (such as refrigerant). The compression mechanism includes a movable scroll and a fixed scroll. When the scroll compressor is running, the drive shaft drives the movable scroll relative to the fixed scroll. The orbiting relative motion enables the movable scroll and the fixed scroll to maintain dynamic engagement with each other, thereby forming a series of compression chambers between the movable scroll and the fixed scroll to compress the working fluid.

Generally, the working fluid inevitably carries impurities. When these impurities enter the compression chamber, they may wear the orbiting scroll and the fixed scroll. In order to solve this problem, an eccentric liner is usually installed between the drive shaft and the orbiting scroll. The sleeve provides a certain range of radial flexibility for the movable scroll, which is to prevent the scroll from being worn out by rigid contact with impurities by making the movable scroll have a radial tolerance that can be slightly translated in the radial direction. . However, when installing the eccentric bushing to the drive shaft, it is necessary to ensure the correct assembly angle between the eccentric bushing and the drive shaft. If installed incorrectly, the scroll compressor will not work properly and will not provide proper radial flexibility. To this end, the prior art provides various technical solutions, but these existing technical solutions often have disadvantages such as requiring additional components or complicated structures, difficult to process, or insufficient strength, and still need to be further improved.

Therefore, the present disclosure provides a scroll compressor with a simpler structure, capable of ensuring the correct installation of the eccentric bushing, and capable of reliably defining the deflection angle of the eccentric bushing to better provide radial flexibility.

Summary of the invention

The general summary of the present disclosure is provided in this section, rather than a comprehensive disclosure of the full scope of the present disclosure or all the features of the present disclosure.

The purpose of the present disclosure is to improve one or more technical problems mentioned above. In general, the present disclosure provides a scroll compressor including:

A compression mechanism, the compression mechanism is adapted to compress a working fluid and includes a fixed scroll and a movable scroll, and the movable scroll includes a drive coupling part;

A drive shaft, the drive shaft including a shaft end surface and a drive portion extending from the shaft end surface; and

An eccentric bush, which is provided between the drive coupling part and the drive part, so that the power of the drive shaft can be transmitted to the movable scroll via the eccentric bush, the eccentric bush The sleeve includes an end surface of the sleeve facing the end surface of the shaft,

It is characterized in that the end face of the bushing includes a first form-fitting part, the end face of the shaft includes a second form-fitting part, and the first form-fitting part and the second form-fitting part cooperate with each other to define the eccentric bushing The deflection angle range of the sleeve relative to the drive shaft.

In the scroll compressor according to the present disclosure, the deflection angle of the eccentric bushing relative to the driving shaft is defined by arranging corresponding shape matching parts on the shaft end surface of the drive shaft and the bushing end face of the eccentric bushing Range without using a third member, so the structure is simpler and the abutting limit is more reliable; in addition, because this limit structure is not provided on the eccentric pin itself and the cylinder of the eccentric bushing with weaker structural strength It is set between the end face of the shaft and the end face of the bushing with greater structural strength, so the strength of the limit structure is more reliable, and will not affect the normal operation of the eccentric pin itself and the bushing body, which play a key transmission role. .

According to a preferred embodiment of the present disclosure, the first form-fitting part is one of a convex part and a concave part, and the second form-fitting part is the other of the convex part and the concave part.

According to a preferred embodiment of the present disclosure, the convex portion and the concave portion are configured such that the convex portion is arranged in the concave portion so as to be contacted by the inner side wall of the concave portion and the outer side wall of the convex portion. The range of the deflection angle is limited.

According to a preferred embodiment of the present disclosure, the outer side wall of the convex portion includes a groove and a cushioning pad located in the groove. By providing such grooves and cushions, the outer side wall of the convex portion does not directly contact the inner side wall of the concave portion, but only the cushion pad in the outer side wall of the convex portion contacts the inner side wall of the concave portion, which not only avoids the outer side wall of the convex portion The abrasion between the inner side wall of the concave portion and the abrasion can provide a buffer for the contact between the outer side wall of the convex portion and the inner side wall of the concave portion, and the buffer pad can be easily replaced when needed, which greatly prolongs the service life.

According to a preferred embodiment of the present disclosure, the driving portion is an eccentric pin, the eccentric pin deviates from the rotation axis of the drive shaft, the eccentric bushing includes an eccentric hole for the eccentric pin to pass through, the eccentric The hole is offset from the center of the eccentric bushing.

According to a preferred embodiment of the present disclosure, the first form-fitting part is the convex part provided at one side of the eccentric hole, and the second form-fitting part is provided at one side of the eccentric pin At the recesses.

According to a preferred embodiment of the present disclosure, the first form-fitting portion is formed as the convex portion that is substantially trapezoidal when viewed in the direction of the rotation axis, and the convex portion has the straight outer side wall, The second form-fitting portion is formed as the recessed portion that is substantially fan-shaped when viewed in the direction of the rotation axis, and the recessed portion has the straight inner side wall.

Since the outer side wall of the convex part and the inner side wall of the recessed part are both straight, the outer side wall and the inner side wall are in planar contact when they abut, there is no uneven abutment such as sharp corners between each other, and they have a larger abutment. The contact area can reduce the wear caused by collision or friction, and make the contact between the two more reliable.

According to a preferred embodiment of the present disclosure, the first form-fitting part is the annular convex part formed around the eccentric hole, and the second form-fitting part is an arc shaped convex part formed around the eccentric pin.調定部。 Said the concave part.

According to a preferred embodiment of the present disclosure, the first form-fitting part is the annular recess formed around the eccentric hole, and the second form-fitting part is the annular convex part formed around the eccentric pin. Department.

Through such a configuration, a smooth and arc-transitioned contact surface can be formed between the outer side wall of the convex portion and the inner side wall of the concave portion, which can better reduce the possibility between the outer side wall of the convex portion and the inner side wall of the concave portion. Wear.

According to a preferred embodiment of the present disclosure, the scroll compressor further includes a counterweight portion attached to one side of the outer peripheral wall of the eccentric bushing. By providing the counterweight, the dynamic balance of the scroll compressor is effectively realized while achieving radial flexibility, so that the operation of the compression mechanism is more stable.

According to a preferred embodiment of the present disclosure, the eccentric bushing includes a cylindrical portion and a base having a diameter larger than that of the cylindrical portion, and the end surface of the bushing is arranged at the base. By providing a base with a larger diameter, a larger area of the end face of the bushing is provided, which is beneficial to forming a limiting structure.

In summary, the scroll compressor according to the present disclosure provides at least the following beneficial technical effects: the scroll compressor according to the present disclosure can ensure the correct installation of the eccentric bushing and can limit the deflection angle of the eccentric bushing with respect to the drive shaft. Within a suitable range, the orbiting scroll can be better provided with radial flexibility, and the eccentric bushing of the present disclosure has a simple structure, higher reliability, easy installation, easy processing and manufacturing, and high cost-effectiveness.

Description of the drawings

The aforementioned and additional features and characteristics of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings, which are only examples and are not necessarily drawn to scale. In the drawings, the same reference numerals are used to indicate the same parts. In the drawings:

Fig. 1 shows a longitudinal sectional view of a scroll compressor according to the present disclosure;

2 shows a schematic diagram of the positions of the eccentric bushing and the drive shaft of the scroll compressor according to the present disclosure in normal and unloaded states, in which the center of the eccentric bushing, the rotation axis of the drive shaft and the eccentric pin are shown in particular The positional relationship between the centers;

Figures 3a-3d show views of the eccentric bushing and the drive shaft in the scroll compressor according to the first embodiment of the present disclosure, wherein Figure 3a shows a perspective view of the eccentric bushing and the drive shaft fitted together. 3b shows the AA longitudinal sectional view of the eccentric bushing and the drive shaft fitted together, Figure 3c shows the BB transverse sectional view of the eccentric bushing and the drive shaft fitted together, and Figure 3d shows the eccentric bushing and the drive shaft separated 'S three-dimensional view;

Figures 4a-4f show views of the eccentric bushing and the drive shaft in the scroll compressor according to the second embodiment of the present disclosure, wherein Figure 4a shows a perspective view of the eccentric bushing and the drive shaft being fitted together. 4b shows a side view of the eccentric bushing and the drive shaft fitted together, Figure 4c shows the AA longitudinal cross-sectional view of the eccentric bushing and the drive shaft fitted together, and Figure 4d shows the eccentric bushing and the drive shaft fitted in BB transverse cross-sectional view together, Figure 4e shows a perspective view of the eccentric bushing and the drive shaft separated, and Figure 4f shows another BB transverse cross-sectional view of the eccentric bushing and the drive shaft fitted together;

Figures 5a and 5b show a further improved embodiment based on the second embodiment shown in Figures 4a-4f, wherein Figure 5a shows a longitudinal sectional view of the eccentric bushing and the drive shaft fitted together, Figure 5b Shows a transverse cross-sectional view of the eccentric bushing and the drive shaft fitted together;

Figures 6a-6c show views of the eccentric bushing and the drive shaft in the scroll compressor according to the third embodiment of the present disclosure, wherein Figure 6a shows a perspective view of the eccentric bushing and the drive shaft separated, and Figure 6b shows A longitudinal cross-sectional view of the eccentric bushing and the drive shaft assembled together, Figure 6c shows a transverse cross-sectional view of the eccentric bushing and the drive shaft assembled together;

Figures 7a and 7b show a further improved embodiment based on the third embodiment shown in Figures 6a-6c, wherein Figure 7a shows a longitudinal sectional view of the eccentric bushing and the drive shaft fitted together, Figure 7b Shows a transverse cross-sectional view of the eccentric bushing and the drive shaft fitted together.

Reference mark list

Scroll compressor 1; housing 12; stator 14; rotor 15; drive shaft 16; main bearing seat 40

Compression mechanism CM; cover 26; base 28; oil sump O; high-pressure space A2; low-pressure space A1

Diaphragm 19; intake pipe 18; exhaust pipe 17; orbiting scroll 24; fixed scroll 22

Fixed scroll end plate 221; fixed scroll scroll S2; orbiting scroll end plate 241; orbiting scroll scroll S4

Hub 240; exhaust port C; drive shaft 16; rotation axis L; shaft end surface 62; eccentric pin 60

Eccentric bushing 11; eccentric hole 10; bushing end face 21; center C1 of eccentric pin 60

The center C2, C2' of the eccentric bushing 11; the cylinder part 110 of the eccentric bushing 11

Base 112 of eccentric bushing 11; recesses 164, 164'

The inner side walls 1640, 1640' of the recesses 164, 164'

Convex part 114, 114'; outer side wall 1140, 1140' of convex part 114, 114'

Groove 113; cushion 1130

Detailed ways

The preferred embodiments of the present disclosure will now be described in detail with reference to FIGS. 1-7b. The following description is merely exemplary in nature and is not intended to limit the present disclosure and its applications or uses.

For ease of description, the scroll compressor shown in FIG. 1 is exemplarily shown as a low-pressure side scroll compressor—that is, the compression mechanism is located in a low-pressure space, but the scroll compressor according to the present disclosure is not limited to this Type, the present disclosure is also applicable to other suitable types of scroll compressors, such as the high-pressure side scroll compressor, where the compression mechanism is located in the high-pressure space.

Fig. 1 shows a longitudinal cross-sectional view of a scroll compressor according to the present disclosure. First, the overall structure of the scroll compressor according to the present disclosure will be briefly described with reference to FIG. 1.

As shown in Figure 1, the scroll compressor 1 includes a substantially cylindrical casing 12, an electric motor (including a stator 14 and a rotor 15), a drive shaft 16, a main bearing housing 40, and a working fluid suitable for compressing a working fluid (such as a refrigerant). ) Compression mechanism CM.

The cover 26 at the top of the housing 12 and the base 28 at the bottom of the housing 12 may be mounted to the housing 12 so as to define the internal volume of the scroll compressor 1. Lubricants such as lubricating oil may be stored in an oil pool O in the bottom of the internal volume for lubricating various relevant components of the scroll compressor 1.

The scroll compressor 1 further includes a partition 19 arranged between the top cover 26 and the casing 12 to partition the internal space of the scroll compressor 1 into a high-pressure space A2 and a low-pressure space A1, specifically, the partition 19 and the cover A high-pressure space A2 is formed between 26, and a low-pressure space A1 is formed between the partition 19, the housing 12, and the base 28. The housing 12 in the low-pressure space A1 is provided with an intake pipe 18 for introducing the low-pressure working fluid to be compressed, and the high-pressure space A2 is provided with a device for discharging the compressed high-temperature and high-pressure fluid to the outside of the scroll compressor 1. Exhaust pipe 17. As mentioned above, the embodiment shown in FIG. 1 is an example of a low-pressure side scroll compressor. Therefore, as shown in FIG. 1, the compression mechanism CM is located in the low-pressure space A1.

The compression mechanism CM includes a movable scroll 24 and a fixed scroll 22. The fixed scroll 22 includes a fixed scroll end plate 221 and a fixed scroll scroll S2; the movable scroll 24 includes a movable scroll end plate 241, a movable scroll scroll S4 extending from the first side surface of the movable scroll end plate 241, and A hub 240 extends from the second side surface of the orbiting scroll end plate 241. The compression mechanism CM is formed with an open suction chamber in fluid communication with the outside of the compression mechanism CM, and the air inlet of the suction chamber is in fluid communication with the low-pressure space A1 in the housing 12 so as to connect the low-pressure space A1 in the low-pressure space A1. The working fluid to be compressed is introduced into the compression mechanism CM; a series of compression chambers formed by the engagement of the fixed scroll scroll S2 and the movable scroll scroll S4 with a volume gradually decreasing from the radial outer side to the radial inner side; and located at the fixed scroll end The exhaust port C at the radial center of the plate 221 can be in fluid communication with the high-pressure space A2 in the housing 12 and discharge the compressed high-temperature and high-pressure fluid into the high-pressure space A2.

On the contrary, for the high-pressure side scroll compressor, the compression mechanism CM is located in the high-pressure space. The compression mechanism CM directly introduces low-pressure working fluid from the outside through a suction fluid pipe and discharges the compressed high-temperature and high-pressure fluid into the internal volume of the housing. The entire internal volume forms a high-pressure space. Therefore, the operating principles of the high-pressure-side scroll compressor and the low-pressure-side scroll compressor are basically the same, but the difference lies mainly in the pressure of the space where the compression mechanism CM is located, which will not be repeated here.

The electric motor includes a stator 14 and a rotor 15. The rotor 15 is used to drive the drive shaft 16 to rotate the drive shaft 16 around its rotation axis L, and the drive shaft 16 is coupled to the movable scroll 24 to drive the movable scroll 24. Specifically, the fixed scroll 22 is mounted to the main bearing housing 40 using mechanical fasteners, for example, to restrict the radial and circumferential movement of the fixed scroll 22 but allow the fixed scroll 22 to perform a certain degree of axial translation, and the movable scroll The orbiting 24 is driven by the electric motor via the drive shaft 16, so that it can perform translational rotation relative to the fixed scroll 22 by means of, for example, an Oldham ring—that is, orbit (that is, the axis of the movable scroll 24 is relative to the fixed scroll 22). The axis revolves, but the orbiting scroll 24 itself does not rotate around its axis—that is, spinning), so that the fixed scroll S2 and the orbiting scroll S4 are joined to form a series of volumes that gradually decrease from the radial outside to the radial inside. Small compression cavity.

As mentioned above, in order to avoid or reduce the wear of the fixed scroll S2 and the movable scroll S4 by impurities, for example, an eccentric bushing is usually provided to realize the radial direction of the movable scroll 24 in a certain range in the radial direction. Flexibility, so that when there are impurities between the fixed scroll scroll S2 and the movable scroll scroll S4, the movable scroll 24 can avoid rigid contact between the scroll and the impurities through flexible translation in the radial direction, thereby significantly reducing or avoiding the scroll. Abraded by impurities, greatly extending the service life.

The eccentric bushing may be coupled between the movable scroll 24 and the driving shaft 16 in various suitable ways, so as to transmit the driving action of the driving shaft 16 to the movable scroll 24 and provide radial flexibility for the movable scroll 24.

Specifically, as shown in FIG. 1, in the present disclosure, the shaft end surface 62 of the first end (upper end) of the drive shaft 16 includes an eccentric pin 60, and the eccentric bushing 11 has an eccentric hole 10 for the eccentric pin 60 to pass through. In this way, the bushing end face 21 of the eccentric bushing 11 is seated on the shaft end face 62 of the drive shaft 16, and a limit part is provided between the eccentric bushing 11 and the drive shaft 16 (not shown in the figure, which will be detailed below) Description), thereby limiting the deflection angle range of the relative deflection between the eccentric bushing 11 and the drive shaft 16 in the circumferential direction. In particular, the eccentric pin 60 is deviated from the rotation axis L of the drive shaft 16. Therefore, under normal circumstances, as the drive shaft 16 rotates, the eccentric bushing 11 as a whole will rotate with the rotation of the drive shaft 16, while the eccentric bushing The center of the sleeve 11 revolves around the rotation axis L, and under special circumstances, the eccentric sleeve 11 can rotate a certain angle relative to the drive shaft 16 (the angle is restricted by the limit portion), thereby realizing the radial flexibility of the movable scroll. In particular, the eccentric bushing 11 is provided between the drive coupling portion of the movable scroll 24 and the eccentric pin 60 of the drive shaft 16, and the drive coupling portion is preferably a hub 240 extending from the back of the orbiting scroll end plate 241, eccentric The bushing 11 is sleeved in the hub 240 as shown in the figure, so that the two can rotate relative to each other, so that when the eccentric bushing 11 is driven by the drive shaft 16 to rotate integrally with the eccentric pin 60, the cross slide Under the action of the ring, the eccentric bushing 11 drives the orbiting scroll 24 to revolve around the rotation axis L of the drive shaft 16 via the drive bearing between the eccentric bushing 11 and the hub 240—that is, orbiting. At the same time, since the fixed scroll 22 is fixed such that the center of the fixed scroll 22 coincides with the rotation axis L of the drive shaft 16, the movable scroll 24 orbits relative to the fixed scroll 22.

Further, as mentioned above, the eccentric bushing 11 not only transmits the driving action of the drive shaft 16 to the movable scroll 24, but also provides radial flexibility for the movable scroll 24. 2 shows a schematic diagram of the position of the eccentric bushing 11 and the drive shaft 16 of the scroll compressor 1 according to the present disclosure in normal and unloaded states, in which the center of the eccentric bushing 11, The positional relationship between the rotation axis of the drive shaft 16 and the center of the eccentric pin. The figure shows the rotation axis L of the drive shaft 16, in addition, C1 represents the center of the eccentric pin 60 (that is, the center of the eccentric hole 10 of the eccentric bushing 11), and C2 and C2' represent the center of the eccentric bushing 11 It can be seen that the eccentric hole 10 of the eccentric bushing 11 deviates from the centers C2 and C2' of the eccentric bushing 11. Therefore, when an external force is applied—for example, impurities in the compression mechanism CM push the scroll, and then push it radially When the orbiting scroll 24 is pressed, the orbiting scroll 24 pushes the eccentric bushing 11 via the hub 240, and the eccentric bushing 11 can be deflected around the center C1 of the eccentric pin 60. For example, as shown in the figure, the center of the eccentric bushing 11 is from C2 is deflected to C2' (the distance from C2' to L is less than the distance from C2 to L), so that the external force can be released, so as to avoid the scroll and the impurities from being rigidly squeezed and worn, thereby realizing the radial direction of the orbiting scroll 24 Flexible.

In order to ensure that the compression mechanism can work normally and that this radial flexibility can be properly provided, the correct installation angle between the eccentric bushing 11 and the drive shaft 16 needs to be ensured, and the eccentric bushing 11 needs to be relative to the drive shaft 16 ( Specifically, the deflection angle relative to the eccentric pin 60) is limited to an appropriate predetermined angle range. The predetermined angle range should be able to provide sufficient radial flexibility (that is, the predetermined angle range should not be too small), while avoiding the deviation to reach the dead center of rotation of the eccentric bushing 11 (that is, the predetermined angle range should not be too large) to ensure Normal operation.

For this reason, the present disclosure sets a limit part between the eccentric bushing 11 and the drive shaft 16, so as to ensure the correct installation angle between the eccentric bushing 11 and the drive shaft 16 during assembly in a reliable and simple manner, and ensure that the During operation, under special circumstances, it is ensured that the eccentric bushing 11 is properly deflected relative to the drive shaft 16 (specifically, relative to the eccentric pin 60) (that is, the deflection angle is limited to an appropriate predetermined angle range). Specifically, the limiting part includes: a first form-fitting part on the end face 21 of the bushing; and a second form-fitting part on the shaft end face 62, the first form-fitting part and the second form-fitting part The portion is configured to limit the fitting angle between the eccentric bushing 11 and the drive shaft 16 along the shaft end surface 62 within a continuously varying predetermined angle range through the shape matching with each other. The first form-fitting part and the second form-fitting part may be structural parts of any shape conceivable by a person of ordinary skill in the art, as long as the technical purpose can be achieved.

Hereinafter, three preferred embodiments according to the present disclosure will be described in detail with reference to the accompanying drawings 3a-7b. These embodiments are only exemplary and are not intended to limit the protection scope of the present disclosure.

Figures 3a-3d show views of the eccentric bushing 11 and the drive shaft 16 in the scroll compressor 1 according to the first embodiment of the present disclosure, wherein Figure 3a shows that the eccentric bushing 11 and the drive shaft 16 are fitted in Figure 3b shows the AA longitudinal cross-sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together, Figure 3c shows the BB transverse cross-sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together, Figure 3d A perspective view showing the separation of the eccentric bush 11 and the drive shaft 16 is shown.

As shown in Figures 3a-3d, the cylindrical portion 110 of the eccentric bushing 11 for coupling the hub 240 of the movable scroll 24 is approximately cylindrical, and the base 112 of the eccentric bushing 11 is disc-shaped and has a relatively larger shape. The bottom surface of the disc-shaped base 112—that is, the bushing end surface 21—is seated on the shaft end surface 62 of the drive shaft 16. By providing a base 112 with a larger diameter, a larger diameter The bushing end face 21 with a large area facilitates the formation of the limiting portion. The eccentric pin 60 of the drive shaft 16 passes through the eccentric hole 10 of the eccentric bush 11, the center C1 of the eccentric pin 60 deviates from the rotation axis L of the drive shaft 16, and the center of the eccentric hole 10—that is, the center C1 of the eccentric pin 60— -Slightly deviate from the center C2 of the eccentric bushing 11, it should be noted that the center C2 of the eccentric bushing 11 is based on the center C2 of the cylinder part 110 of the eccentric bushing 11, because the cylinder part 110 directly contacts the movable vortex The hub 240 of the spin 24 is slightly deviated from the center C2 of the cylindrical portion 110 of the eccentric bushing 11 by making the center of the eccentric hole 10 of the eccentric bushing 11, that is, the center C1 of the eccentric pin 60, and making the eccentric bushing The sleeve 11 (the barrel portion 110) is deflected by a certain angle around the eccentric pin 60, so that the radial flexibility as described above can be realized.

As best shown in FIGS. 3c and 3d, a recess 164 is provided on one side of the eccentric pin 62 of the drive shaft 16. The recess 164 is a fan-shaped tapered recess and includes an inner side wall 1640, which is implemented here In this manner, the inner side wall 1640 is configured as a straight inner side wall. A trapezoidal tapered convex portion 114 is correspondingly provided on one side of the eccentric hole 10 of the eccentric bushing 11, and the convex portion 114 has a straight outer side wall 1140. When the eccentric bushing 11 is installed to the drive shaft 16, the convex portion 114 is placed in the concave portion 164 and can move in the concave portion 164 within the angular range defined by the inner side wall 1640 of the concave portion 164, and the inner side wall 1640 of the concave portion 164 passes through the abutment. The outer side wall 1140 of the convex portion 114 is connected to limit the movement range of the convex portion 114.

It should be noted here that although in the illustrated embodiment, the above-mentioned "trapezoid" is in a stricter trapezoidal shape, it should be understood by those of ordinary skill in the art that the present disclosure actually covers "in the eccentric bushing 11 One side of the eccentric hole 10 is correspondingly provided with a substantially trapezoidal tapered convex portion 114". The “substantially trapezoidal” is intended to emphasize that the convex portion is tapered or “substantially trapezoidal” as a whole. The shape, while allowing the part to be curved or inconsistent in the inclination of the part, is not strictly limited to a trapezoidal shape. Similarly, the term "fan-shaped" in the text also covers the case of "roughly fan-shaped".

In particular, in this embodiment, the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164 are both straight and have a uniform slope, so that the outer side wall 1140 and the inner side wall 1640 are in plane contact when they abut. , There is no sharp corners and other uneven abutment between each other, and a larger contact area, which can reduce the wear caused by collision or friction, and make the abutment between the two more reliable.

It should be understood that the first form-fitting part (convex part) according to the present disclosure may be a boss with a straight, tapered, arc-shaped or special-shaped outer side wall, and the second form-fitting part (concave part) may have a flat outer wall. The recesses of the straight, tapered, arc-shaped or special-shaped inner side wall can be set by those of ordinary skill in the art according to actual needs.

Figures 4a-4f show views of the eccentric bushing 11 and the drive shaft 16 in the scroll compressor 1 according to the second embodiment of the present disclosure, wherein Figure 4a shows that the eccentric bushing 11 and the drive shaft 16 are fitted in Fig. 4b shows a side view of the eccentric bushing 11 and the drive shaft 16 fitted together, Fig. 4c shows the AA longitudinal sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together, and Fig. 4d shows The BB transverse cross-sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together, Figure 4e shows a perspective view of the eccentric bushing 11 and the drive shaft 16 separated, and Figure 4f shows the eccentric bushing 11 and the drive shaft 16 fitted together Another cross-sectional view of BB.

As shown in Figures 4a-4f, this embodiment is basically the same as the aforementioned first embodiment. The cylindrical portion 110 of the eccentric bushing 11 for coupling the hub 240 of the movable scroll 24 is substantially cylindrical, and the eccentric bushing 11 The base 112 has a disk shape and has a relatively larger cross-sectional area. The bushing end face 21 is seated on the shaft end face 62 of the drive shaft 16, and the eccentric pin 60 of the drive shaft 16 passes through the eccentric hole 10 of the eccentric bushing 11. , The center C1 of the eccentric pin 60 deviates from the rotation axis L of the drive shaft 16, and the center of the eccentric hole 10, that is, the center C1 of the eccentric pin 60, is slightly deviated from the center C2 of the eccentric bushing 11 (the cylinder portion 110). The difference between this embodiment and the aforementioned first embodiment is that the recess 164 on the shaft end surface 62 of the drive shaft 16 is set as an arc-shaped recess formed around the eccentric pin 60. Accordingly, the bush end surface 21 of the eccentric bush 11 The upper convex portion 114 is set as an annular boss formed around the eccentric hole 10. Therefore, the concave portion 164 has an inner side wall 1640. In the second embodiment, the inner side wall 1640 is set in an arc shape, and the convex portion 114 may have a circular shape or an elliptical shape. Shaped outer side wall 1140, more preferably, the convex portion 114 has a round outer side wall 1140.

As shown in FIG. 4d, within the normal installation angle range, there is a certain gap between the convex portion 114 and the concave portion 164, and when the movable scroll is radially pressed by an external force (such as impurities), the convex portion 114 It can move a certain predetermined angle in the recess 164, thereby providing radial flexibility. And, preferably, by providing the convex portion 114 to have a circular outer side wall 1140, and the concave portion 164 has an arc-shaped inner side wall 1640, it can be formed between the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164. The smooth and arc-transitioned contact surface can better reduce possible wear between the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164.

As mentioned above, the eccentric bushing 11 can be deflected around the center C1 of the eccentric pin 60. For example, as shown in FIG. Distance), so that the radial flexibility of the movable scroll 24 can be achieved. In order to better realize this deflection of the center of the eccentric bushing 11, generally, the convex portion 114 is arranged eccentrically with respect to the eccentric hole 10, so that the deflection of the convex portion 114 in the concave portion 164 becomes the center band of the eccentric bushing 11 To achieve a larger deflection range, and therefore the convex portion 114 can also be eccentric with respect to the cylindrical portion 110 of the eccentric bushing 11, but it is easy to think that, depending on the actual situation, the convex portion 114 is different from the eccentric hole 10 and the cylindrical body. The positional relationship of the three parts 110 can have various changes, as long as the technical purpose of the present disclosure can be achieved.

In particular, as shown in FIG. 4f, the convex portion 114 and the concave portion 164 may be more preferably configured such that when the convex portion 114 moves in the concave portion 164 within a predetermined angle range, the outer wall 1140 of the convex portion 114 is always maintained. A part of the inner wall 1640 of the concave portion 164 is in contact with a part, that is, during the initial installation and the entire operation of the scroll compressor, a part of the outer wall 1140 of the convex portion 114 is always kept in contact with a part of the inner wall 1640 of the concave portion 164 Specifically, the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164 have a perfectly matched curvature, so that the dynamic joint is always maintained. Therefore, the collision between the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164 can be completely avoided, and the collision between the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164 can be better reduced or even avoided. Possible wear and tear.

Figures 5a and 5b show a further improved embodiment based on the second embodiment shown in Figures 4a-4f, wherein Figure 5a shows a longitudinal sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together, Figure 5b shows a transverse cross-sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together. On the basis of the second embodiment shown in FIGS. 4a-4f, the following improvements are further made: as best shown in FIG. The groove 113, and a cushion 1130 is arranged in the groove 113. In this embodiment, the groove 113 is provided as an annular groove 113 along the entire outer side wall 1140, and the cushion 1130 is in the form of an annular gasket. However, the present disclosure is not limited to this, for example, in the aforementioned first embodiment. Grooves and cushions can be provided on the outer side wall 1140 of the trapezoidal tapered convex portion 114, and only the outer side wall 1140 of the trapezoidal tapered convex portion 114 may contact the inner side wall of the concave portion 164. The 1640 part is provided with such grooves and cushions.

In this embodiment, by providing the groove 113 and the cushion 1130, the outer side wall 1140 of the convex portion 114 does not directly contact the inner side wall 1640 of the concave portion 164, but only the cushion 1130 in the outer side wall 1140 of the convex portion 114 Contact with the inner side wall 1640 of the concave portion 164, which not only avoids the abrasion between the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164, but also between the outer side wall 1140 of the convex portion 114 and the inner side wall 1640 of the concave portion 164 The contact provides cushioning, and the cushion 1130 can be easily replaced when needed, which greatly extends the service life.

In the foregoing two embodiments, the first form-fitting portion on the bushing end surface 21 of the eccentric bushing 11 is the convex portion 114 that protrudes outward, and the second form-fitting portion on the shaft end surface 62 of the drive shaft 16 is both It is the concave recess 164 as described above, but the present disclosure is not limited to this. For example, FIGS. 6a-6c show the eccentric bushing 11 and the drive in the scroll compressor 1 according to the third embodiment of the present disclosure. A view of the shaft 16, wherein Figure 6a shows a perspective view of the eccentric bushing 11 and the drive shaft 16 separated, Figure 6b shows a longitudinal sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together, and Figure 6c shows the eccentric bushing A transverse cross-sectional view of the sleeve 11 and the drive shaft 16 fitted together.

As shown in FIGS. 6a-6c, the difference between this embodiment and the previous two embodiments is that the first form-fitting portion on the bushing end surface 21 of the eccentric bushing 11 is configured as an annular recess 164 formed around the eccentric hole 10 ', and the second form-fitting portion on the shaft end surface 62 of the drive shaft 16 is configured as an annular convex portion 114' formed around the eccentric pin 60, and the concave portion 164' may have a circular or elliptical inner side wall 1640', The convex portion 114' may have a circular or elliptical outer side wall 1140'. Preferably, as shown in FIG. When the scroll compressor is running, the convex portion 114' can move within the concave portion 164' within a predetermined angle range, so as to provide a certain radial flexibility for the movable scroll 24; or, the concave portion 164' can also be larger. Round, the convex portion 114' is a smaller circle, or the concave portion 164' can also be a larger ellipse, and the convex portion 114' is a smaller ellipse, or the concave portion 164' can also be a larger circle. The convex portion 114' has a relatively small elliptical shape and is not particularly limited, as long as the above-mentioned radial flexibility can be achieved.

Figs. 7a and 7b show a further improved embodiment based on the third embodiment shown in Figs. 6a-6c, wherein Fig. 7a shows a longitudinal sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together, Figure 7b shows a transverse cross-sectional view of the eccentric bushing 11 and the drive shaft 16 fitted together. Similar to the embodiment shown in FIGS. 5a and 5b, as best shown in FIG. 7a, in this embodiment, in the outer side wall 1140' of the convex portion 114' on the shaft end surface 62 of the drive shaft 16 A groove 113 is provided, and a cushion 1130 is provided in the groove 113. In this embodiment, the groove 113 is provided as an annular groove 113 along the entire outer side wall 1140', and the cushion 1130 is in the form of an annular gasket. Similarly, by providing the groove 113 and the cushion 1130, not only the abrasion between the outer side wall 1140' of the convex portion 114' and the inner side wall 1640' of the concave portion 164' is avoided, but also the outer side of the convex portion 114' The contact between the wall 1140' and the inner side wall 1640' of the recess 164' provides cushioning, and the cushioning pad 1130 can be easily replaced when needed, which greatly extends the service life.

In each of the foregoing embodiments, the first shape-matching portion and the second shape-matching portion each include only one convex portion or one concave portion. However, the present disclosure is not limited to this, although it may not be a preferred embodiment, it may be For example, one of the first form-fitting part and the second form-fitting part includes two convex parts, and the other of the first form-fitting part and the second form-fitting part It includes two concave parts. When the eccentric bushing and the drive shaft are fitted together, the two convex parts are respectively fitted in the two concave parts and can move in the corresponding concave parts by a predetermined angle, thereby providing radial flexibility; or, the One of the first form-fitting part and the second form-fitting part includes two convex parts, and the other of the first form-fitting part and the second form-fitting part includes a concave part. When the sleeve and the drive shaft are fitted together, the two convex parts are both fitted in the one concave part and can move a predetermined angle in the concave part, thereby providing radial flexibility.

In addition, the scroll compressor 1 according to the present disclosure may further include a counterweight portion (not shown in the figure), which may be attached to one side of the outer peripheral wall of the eccentric bushing 11, specifically, the counterweight For example, the part may be attached to one side of the disc-shaped base 112 of the eccentric bush 11 or be integrally formed with the base 112. The counterweight can be used to improve the center of mass imbalance caused by the processing error of the moving parts (such as the eccentric bushing 11, etc.) and/or other components, for example, due to the deviation of the eccentric bushing 11 from the drive shaft 16 Problems such as unstable motion caused by the rotation axis L of the shaft. By appropriately adjusting the size and position of the counterweight part, this unstable factor can be balanced, and the dynamic balance of the scroll compressor 1 can be effectively achieved while achieving radial flexibility. , So that the operation of the compression mechanism CM is more stable.

Although exemplary embodiments of the scroll compressor according to the present disclosure are described in the foregoing embodiments, the present disclosure is not limited thereto, but various modifications can be made without departing from the protection scope of the present disclosure. Type, replacement and combination.

It is obvious that by combining or modifying different embodiments and various technical features in different ways, various different embodiments can be further designed.

The scroll compressor according to the preferred embodiment of the present disclosure is described above in conjunction with the specific embodiments. It can be understood that the above description is only exemplary and not restrictive. Without departing from the scope of the present disclosure, those skilled in the art can conceive of various variations and modifications with reference to the above description. These variations and modifications are also included in the protection scope of the present disclosure.

Claims

A scroll compressor (1), comprising:

A compression mechanism (CM), the compression mechanism is adapted to compress a working fluid and includes a fixed scroll (22) and a movable scroll (24), the movable scroll includes a drive coupling part;

A drive shaft (16), the drive shaft including a shaft end surface (62) and a drive portion extending from the shaft end surface; and

An eccentric bushing (11), the eccentric bushing is arranged between the driving coupling part and the driving part, so that the power of the driving shaft can be transmitted to the movable scroll via the eccentric bushing, so The eccentric bushing includes a bushing end surface (21) facing the shaft end surface,

It is characterized in that the end face of the bushing includes a first form-fitting part, the end face of the shaft includes a second form-fitting part, and the first form-fitting part and the second form-fitting part cooperate with each other to define the eccentric bushing The deflection angle range of the sleeve relative to the drive shaft.
The scroll compressor according to claim 1, wherein the first shape matching portion is one of a convex portion (114, 114') and a concave portion (164, 164'), and the second shape matching portion is The other of the convex portion and the concave portion.
The scroll compressor according to claim 2, wherein the convex portion and the concave portion are configured such that the convex portion is arranged in the concave portion so as to pass through the inner side wall (1640, 1640') of the concave portion. ) Abutment with the outer side wall (1140, 1140') of the convex portion to define the deflection angle range.
The scroll compressor according to claim 3, wherein the outer side wall of the convex portion includes a groove (113) and a cushion (1130) located in the groove.
The scroll compressor according to any one of claims 2 to 4, wherein the drive portion is an eccentric pin (60), the eccentric pin is offset from the rotation axis (L) of the drive shaft, so The eccentric bushing includes an eccentric hole (10) through which the eccentric pin passes, and the eccentric hole is deviated from the center (C2, C2') of the eccentric bushing.
The scroll compressor according to claim 5, wherein the first form-fitting part is the convex part provided at one side of the eccentric hole, and the second form-fitting part is provided at The recess at one side of the eccentric pin.
The scroll compressor according to claim 6, wherein the first form-fitting portion is formed as the convex portion that is substantially trapezoidal when viewed in the direction of the rotation axis, and the convex portion has a flat surface. For the straight outer side wall, the second form-fitting portion is formed as the recessed portion that is substantially fan-shaped when viewed in the direction of the rotation axis, and the recessed portion has the straight inner side wall.
The scroll compressor according to claim 5, wherein the first shape matching portion is the annular convex portion formed around the eccentric hole, and the second shape matching portion is surrounding the eccentric hole. The arc-shaped recess formed by a pin; or, the first form-fitting part is an annular recess formed around the eccentric hole, and the second form-fitting part is an annular recess formed around the eccentric pin The convex portion.
The scroll compressor according to any one of claims 1 to 4, wherein the scroll compressor further comprises a counterweight portion attached to the outer peripheral wall of the eccentric bushing On the side.
The scroll compressor according to any one of claims 1 to 4, wherein the eccentric bushing includes a cylindrical portion (110) and a base (112) with a diameter larger than the diameter of the cylindrical portion , The end face of the bushing is arranged at the base.