compressor

Abstract

The application provides a compressor, which comprises a rotating shaft, a main bearing seat, a main bearing, a secondary bearing seat and a secondary bearing; the rotating shaft is provided with a central oil channel and an auxiliary oil channel, and the outlet of the auxiliary oil channel is opposite to the inner side wall of the inner ring of the secondary bearing; the rotating shaft comprises a connecting pin, which is arranged eccentrically relative to the shaft center of the rotating shaft; the center point of the projection of the connecting pin on the end face of the rotating shaft and the center point of the rotating shaft are located on a straight line L, the auxiliary oil channel and the straight line L have an included angle θ, and the included angle θ satisfies 0<θ<45°; in the radial direction of the rotating shaft, the opening angle of the included angle θ is towards the side away from the connecting pin. The back pressure cavity, the central oil channel and the auxiliary oil channel are in communication, the included angle θ between the auxiliary oil channel and the straight line L satisfies 0<θ<45°, so that the outlet of the auxiliary oil channel is attached to the inner side wall of the inner ring of the secondary bearing when the one end of the rotating shaft is deflected, lubricating oil can lubricate the secondary bearing, and the back pressure cavity cannot lose pressure.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressor, in particular to a compressor. BACKGROUND

[0002] The compressor structure comprises a dynamic vortex disc, a static vortex disc and a rotating shaft, and the compressor further comprises a suction cavity, a compression cavity and a back pressure cavity. The rotating shaft is connected with the dynamic vortex disc to drive the dynamic vortex disc to rotate and cooperate with the static vortex disc to compress refrigerant gas. The compressor further comprises a bearing assembly for supporting the rotating shaft. In the related art, the rotating shaft of the compressor has a central oil channel arranged along the axial direction thereof and an auxiliary oil channel in communication with the central oil channel. The outlet of the auxiliary oil channel is opposite to the inner side wall of the bearing. Since the rotating shaft drives the dynamic vortex disc to perform eccentric motion when rotating, the end of the rotating shaft away from the dynamic vortex disc will be deflected, so that one side of the end of the rotating shaft is close to the inner side wall of the bearing, and the other side of the end of the rotating shaft is far away from the inner side wall of the bearing to form a large gap. The outlet of the auxiliary oil channel in the related art is located at the side of the gap, which will cause the pressure in the back pressure cavity and the refrigerant leakage, thereby affecting the compression effect of the refrigerant gas. SUMMARY

[0003] The present application provides a compressor which can ensure the compression effect.

[0004] The present application provides a compressor which comprises a rotating shaft, a main bearing seat, a main bearing, a secondary bearing seat and a secondary bearing. One end of the rotating shaft is matched with the main bearing, the main bearing is fixed to the main bearing seat, the other end of the rotating shaft is matched with the secondary bearing, and the secondary bearing is fixed to the secondary bearing seat.

[0005] The rotating shaft has a central oil channel and an auxiliary oil channel, the central oil channel is in communication with the auxiliary oil channel, and the outlet of the auxiliary oil channel is opposite to the inner side wall of the inner ring of the secondary bearing.

[0006] The rotating shaft comprises a connecting pin and a connecting end face. The connecting pin extends away from the central oil channel from the connecting end face, and the connecting pin is eccentrically arranged relative to the axis of the rotating shaft. The center point of the projection of the connecting pin on the connecting end face and the center point of the connecting end face are located on the same straight line. An included angle between the axial direction of the auxiliary oil channel and the straight line is defined as θ, wherein the range of θ is 0 < θ < 45°. The opening angle of the included angle θ is towards the side away from the connecting pin.

[0007] In the present application, the connecting pin is eccentrically arranged relative to the axis of the rotating shaft, and the included angle between the auxiliary oil channel and the straight line is 0 < θ < 45°. When the rotating shaft is subjected to force at one end of the connecting pin, the rotating shaft is deflected at the end of the auxiliary oil channel towards the side opposite to the force, and the outlet of the auxiliary oil channel is fitted to the inner side wall of the inner ring of the secondary bearing. The occurrence of the pressure loss in the back pressure cavity is reduced, thereby ensuring the compression effect. BRIEF DESCRIPTION OF DRAWINGS

[0008] Figure 1 Fig. 1 is a perspective view of a compressor according to the present application;

[0009] Figure 2 Fig. 2 is a perspective sectional view of the compressor according to the present application;

[0010] Figure 3 Fig. 3 is a perspective view of Figure 2 Fig. 4 is an enlarged view of the circle A in Fig. 3;

[0011] Figure 4 Fig. 5 is a perspective view of a connection between a rotating shaft and an eccentric bush according to the present application;

[0012] Figure 5 Fig. 6 is a sectional view of the connection between the rotating shaft and the eccentric bush according to the present application;

[0013] Figure 6 Fig. 7 is an exploded perspective view of the rotating shaft and the eccentric bush according to the present application;

[0014] Figure 7 Fig. 8 is an exploded perspective view of the rotating shaft and the eccentric bush according to the present application, from another angle;

[0015] Figure 8 Fig. 9 is a side view of the rotating shaft according to the present application;

[0016] Figure 9 Fig. 10 is a sectional view of a connection between the rotating shaft and a sub-bearing according to the present application;

[0017] Figure 10 Fig. 11 is a perspective view of the eccentric bush according to the present application;

[0018] Figure 11 Fig. 12 is a perspective view of the eccentric bush according to the present application, from another angle;

[0019] Figure 12 Fig. 13 is a perspective view of a moving scroll according to the present application;

[0020] Figure 13 Fig. 14 is a partial sectional view of the compressor according to the present application. DETAILED DESCRIPTION

[0021] For better understanding of the technical solutions of the present application, the embodiments of the present application are described in detail below with reference to the drawings.

[0022] It should be noted that the described embodiments are only some of the embodiments of the present application, but not all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0023] As Figures 1-7And 9-12 is one of the embodiments of the compressor of the application, which comprises a rotating shaft 1, a main bearing seat 2, a main bearing 201, a secondary bearing seat 3 and a secondary bearing 301, the rotating shaft 1 is matched with the main bearing 201 at one end, the main bearing 201 is fixed on the main bearing seat 2, the rotating shaft 1 is matched with the secondary bearing 301 at the other end, and the secondary bearing 301 is fixed on the secondary bearing seat 3; the compressor comprises a moving vane 4, and the compressor has a back pressure cavity 5, which is located between the moving vane 4 and the main bearing seat 2.

[0024] The main bearing seat 2 and the secondary bearing seat 3 support the rotating shaft 1, so that the rotating shaft 1 can rotate stably under the action of the main bearing 201 and the secondary bearing 301.

[0025] As shown in Figures 2-3 , the rotating shaft 1 has a central oil channel 101 and an auxiliary oil channel 102, the central oil channel 101 is communicated with the auxiliary oil channel 102, the central oil channel 101 is communicated with the back pressure cavity 5, and the outlet of the auxiliary oil channel 102 is opposite to the inner wall of the inner ring of the secondary bearing 301; in the radial direction of the rotating shaft 1, the rotating shaft 1 comprises an outer wall surface 105, the outlet of the auxiliary oil channel 102 penetrates the outer wall surface 105, and the distance between the outer wall surface 105 and the inner wall surface of the inner ring of the secondary bearing 301 is defined as h, wherein the range of h satisfies the following relationship: 0.05mm≤h≤0.5mm.

[0026] The communication between the central oil channel 101 and the back pressure cavity 5 can make the lubricating oil entering the back pressure cavity 5 guided into the central oil channel 101, and then guided into the inner wall of the inner ring of the secondary bearing 301 by the communicated auxiliary oil channel 102, so as to lubricate the secondary bearing 301.

[0027] As shown in Figure 12 , the moving vane 4 comprises an end plate 401 and a spiral wall 402, the end plate 401 has a back pressure hole 403; the compressor further comprises a stationary vane 8, and the compressor has a compression cavity 9 located between the stationary vane 8 and the moving vane 4, the back pressure hole 403 communicates the compression cavity 9 and the back pressure cavity 5, in other words, the moving vane 4 cooperates with the stationary vane 8 to form the compression cavity 9.

[0028] When the refrigerant gas is compressed into the compression chamber 9, the pressure will continue to increase, and the setting of the back pressure hole 403 can introduce part of the pressure in the compression chamber 9 into the back pressure chamber 5. The introduced pressure can form a pressure in the back pressure chamber 5 at the back of the moving scroll 4, thereby resisting the pressure in the compression chamber 9, causing the moving scroll 4 to approach and adhere to the stationary scroll 8, avoiding the problem of separation of the moving scroll 4 and the stationary scroll 8 due to the excessively high pressure in the compression chamber 9, causing the compression refrigerant to leak. The introduction of pressure will also introduce lubricating oil, which can lubricate the components in the back pressure chamber 5. The outlet of the auxiliary oil path 102 is opposite the inner ring side wall of the auxiliary bearing 301, and the distance therebetween is set to be within 0.05mm-0.5mm, which functions to: while ensuring that the auxiliary oil path 102 can guide lubricating oil to the auxiliary bearing 301 for lubrication, it also ensures that the back pressure chamber 5 will not lose pressure. Because if the outlet of the auxiliary oil path 102 is set at the end of the rotating shaft 1, although it can also guide the lubricating oil in the back pressure chamber 5 to the position of the auxiliary bearing 301, at this time the back pressure chamber 5 is prone to lose pressure, which will affect the effect of compression of the refrigerant gas. As a preferred embodiment, when the distance h between the outlet of the auxiliary oil path 102 and the inner ring side wall of the auxiliary bearing 301 is 0.05mm to 0.1mm, the effect is best.

[0029] As shown in Figure 5 , the ratio of the thickness of the inner ring of the auxiliary bearing 301 in the axial direction of the rotating shaft 1 to the aperture of the auxiliary oil path 102 is a, wherein a is in the range of: 4≤a≤8. If the aperture of the auxiliary oil path 102 is greater than the thickness of the auxiliary bearing 301, as described above, although it is possible to guide lubricating oil to the auxiliary bearing 301 for lubrication, it will also cause the back pressure chamber 5 to lose pressure; and if the aperture of the auxiliary oil path 102 is much smaller than the thickness of the auxiliary bearing 301, at this time the amount of lubricating oil guided out of the outlet of the auxiliary oil path 102 will be too small, which will result in poor lubrication effect. By setting the ratio of the thickness of the auxiliary bearing 301 to the aperture of the auxiliary oil path 102 to be 4-8, the amount of oil can be ensured, and at the same time the back pressure chamber 5 will not lose pressure.

[0030] As shown in Figure 2 , the compressor comprises an eccentric bushing 6 located in the back pressure chamber 5; the end of the rotating shaft 1 is provided with a connecting pin 103 which is eccentrically arranged relative to the axis of the rotating shaft 1, the eccentric bushing 6 is connected with the connecting pin 103, and the eccentric bushing 6 is connected with the moving scroll 4 through a bearing.

[0031] The moving scroll 4 is connected at one end of the rotating shaft 1 through the eccentric bushing 6, so that the rotating shaft 1 can drive the moving scroll 4 to move eccentrically, and the entering refrigerant gas is compressed by engaging with the stationary scroll 8, and at the same time the connecting pin 103 is eccentrically connected at the end of the rotating shaft 1, so that the eccentric bushing 6 will also rotate eccentrically under the driving of the rotating shaft 1.

[0032] As Figures 4-7 As shown in Figs. 10 and 11, the eccentric bushing 6 comprises a sleeve part 601 and a counterweight part 602. The sleeve part 601 has a sleeve hole 603 in which the connecting pin 103 is at least partially located. The counterweight part 602 is connected to the peripheral side wall of the sleeve part 601 and is located at the peripheral side of the end of the sleeve part 601 close to the rotating shaft 1. The peripheral side wall of the counterweight part 602 has an arc-shaped groove 604 in which the end of the rotating shaft 1 is at least partially located. The sleeve hole 603 is eccentrically arranged relative to the axis of the sleeve part 601.

[0033] The sleeve part 601 is arranged to facilitate the connection with the connecting pin 103, and the counterweight part 602 is arranged to balance the centrifugal force generated by the action of the moving scroll 4 when the moving scroll 4 moves eccentrically. The arc-shaped groove 604 provides a point of abutment for the end of the rotating shaft 1, and the shape of the arc-shaped groove 604 is adapted to the end of the rotating shaft 1. When the end of the rotating shaft 1 abuts into the arc-shaped groove 604, the arc-shaped groove 604 can limit the eccentric bushing 6, so that the eccentric bushing 6 can only rotate with the rotating shaft 1 and cannot rotate by itself, thereby making the structure more stable.

[0034] As Figures 10-11 shown, the cross-sectional shape of the counterweight part 602 is a sector. In the radial direction of the rotating shaft 1, the counterweight part 602 and the connecting pin 103 are located on opposite sides of the axis of the rotating shaft 1.

[0035] The shape of the counterweight part 602 is not limited to a sector, and can be an ellipse, a square, etc. The sector is arranged to facilitate machining, facilitate measurement of the position of the center of gravity, and save space inside the compressor due to the structural characteristics of the sector. The counterweight part 602 is arranged on the opposite side of the connecting pin 103 because the centrifugal force generated by the rotating connecting pin 103 after the moving scroll 4 is connected can be balanced by the counterweight part 602 on the opposite side.

[0036] The sleeve part 601 has an inner notch 605 located at the orifice position of the sleeve hole 603 close to the rotating shaft 1. The inner notch 605 is in communication with the back pressure cavity 5 and is at least partially in communication with the central oil passage 101.

[0037] The inner notch 605 can effectively communicate the central oil passage 101 and the back pressure cavity 5, and can serve as a transition communication. If there is no inner notch 605, the inlet of the central oil passage 101 will be blocked due to the abutment of the sleeve part 601 and the end of the rotating shaft 1. Even if lubricating oil can enter the central oil passage 101 from the gap between the sleeve part 601 and the end of the rotating shaft 1, the amount of oil entering will be very small, and the sub-bearing 301 cannot be lubricated.

[0038] As Figure 2 and 10As shown in -11, the eccentric bushing 6 includes an extension 606, which extends from the counterweight 602 near the moving scroll 4 in an axial direction parallel to the rotating shaft 1.

[0039] The extension 606 is also designed to balance the centrifugal force generated by the eccentrically moving scroll 4. The moving scroll 4 is connected to the connecting pin 103 via the eccentric bushing 6, so its overall center of gravity is closer to the stationary scroll 8. The extension 606 also extends towards the moving scroll 4, which effectively balances the offset of the moving scroll 4's center of gravity. If the extension 606 extended towards the opposite side of the moving scroll 4, the centrifugal force generated when the moving scroll 4 moves and the centrifugal force generated when the extension 606 is driven to rotate would be further apart in the axial direction of the rotating shaft 1, making it difficult to balance and detrimental to structural stability.

[0040] like Figure 2 As shown, the compressor includes a balance block 7. The center of gravity of the balance block 7 and the counterweight 602 is located on the same side of the axis of the rotating shaft 1. The balance block 7 is installed on the side wall of the rotating shaft 1. The function of the balance block 7 is the same as that of the counterweight 602, which is to balance the centrifugal force generated by the eccentric movement of the moving scroll 4.

[0041] like Figure 2 As shown, the compressor includes a housing 10, a stator 11, and a rotor 12. The stator 11 is connected to the inner wall of the housing 10, and the rotor 12 is connected to the shaft 1. The rotor 12 is at least partially located inside the stator 11. The stator 11 is electrically connected to an external circuit. When energized, the electromagnetic driving force generated by the stator 11 and the rotor 12 drives the shaft 1 to rotate, thereby driving the eccentric bushing 6 and the moving scroll 4 to move.

[0042] In another embodiment, such as Figure 8 As shown, the connecting pin 103 is eccentrically positioned relative to the axis of the rotating shaft 1; the rotating shaft 1 includes a connecting end face 106, and the connecting pin 103 extends from the connecting end face 106 away from the central oil passage. The center point of the projection of the connecting pin 103 onto the connecting end face 106 and the center point of the connecting end face 106 are located on the same straight line L. The angle between the axial direction of the auxiliary oil passage 102 and the straight line L is defined as θ, where the range of θ is: 0 < θ < 45°; the angle θ is oriented towards the side away from the connecting pin 103.

[0043] like Figure 5 and 8As shown, after the moving scroll 4 is connected to the connecting pin 103 through the eccentric bushing 6, the connecting pin 103 can be driven to rotate eccentrically by the rotating shaft 1, at this time, the moving scroll 4 will generate a centrifugal force F1 under the eccentric action, since the moving scroll 4 is located at one end of the rotating shaft 1, at this time, the centrifugal force F1 will generate a prying action on the rotating shaft 1 with the main bearing 201 as the fulcrum, so that the other end of the rotating shaft 1 moves in the direction opposite to the centrifugal force F1, and further, the other end of the rotating shaft 1 generates an acting force F2 on the auxiliary bearing 301, the direction of the acting force F2 is opposite to that of the centrifugal force F2; when the other end of the rotating shaft 1 is attached to the inner side wall of the inner ring of the auxiliary bearing 301, the outlet of the auxiliary oil passage 102 is also attached to the inner side wall of the inner ring of the auxiliary bearing 301, thereby preventing the back pressure cavity 5 from losing pressure, at this time, although the outlet of the auxiliary oil passage 102 is attached to the inner side wall of the inner ring of the auxiliary bearing 301, the lubricating oil in the back pressure cavity 5 can still be guided to the outlet of the auxiliary oil passage 102 through the central oil passage 101, and the lubricating oil will be coated on the inner side wall of the inner ring of the auxiliary bearing 301 with the rotation of the rotating shaft 1, thereby achieving lubrication.

[0044] As shown in Figure 5 and Figure 8 in the radial direction of the rotating shaft 1, if the opening angle θ is directed to the side of the connecting pin 103, the connecting pin 103 will generate a centrifugal force F1 under force, at this time, the rotating shaft 1 will still generate an acting force F2 in the opposite direction at the end where the auxiliary oil passage 102 is located, but at this time, the outlet of the auxiliary oil passage 102 will be away from the inner side wall of the inner ring of the auxiliary bearing 301, the distance between them will be increased, the smoothness of the flow of the auxiliary oil passage 102 will be improved, at this time, the back pressure cavity 5 will easily lose pressure, which will affect the compression effect.

[0045] Preferably, the auxiliary oil passage 102 has an opening angle θ between the axial direction and the straight line L, 0 < θ ≤ 10°, at this time, the effect is best.

[0046] As shown in Figures 2-3 and 7, the end of the rotating shaft 1 opposite to the inner recess 605 has a chamfer 104. The chamfer 104 can increase the communication area between the inner recess 605 and the back pressure cavity 5, and improve the smoothness of the flow of the lubricating oil.

[0047] As shown in Figures 1-2 , the compressor comprises a housing 10, the housing 10 and the exhaust cover 13 are respectively connected to the two ends of the main bearing seat 2 along the axial direction, the compressor has a suction chamber 14, the suction chamber 14 is located between the main bearing seat 2 and the housing 10; the auxiliary bearing seat 3 has a hole 303, the auxiliary bearing seat 3 has a cavity 302, the hole 303 communicates the suction chamber 14 and the cavity 302.

[0048] The suction chamber 14 is filled with lubricating oil, and when refrigerant gas enters, it entrains the lubricating oil and flows inside. The hole 303 is arranged to allow the refrigerant gas mixed with the lubricating oil to enter the cavity 302, thereby lubricating the sub-bearing 301.

[0049] As shown in Figure 13 The compressor has a high-pressure chamber 15 between the stationary scroll 8 and the exhaust cover 13, and the high-pressure chamber 15 is in communication with the compression chamber 9. The exhaust cover 13 has an oil separation chamber 16 in communication with the high-pressure chamber 15. The exhaust cover 13 has a first oil passage 17, and the main bearing seat 2 has a second oil passage 18. The first oil passage 17 is in communication with the oil separation chamber 16, and the first oil passage 17 is in communication with the second oil passage 18. The second oil passage 18 is in communication with the back-pressure chamber 5.

[0050] The lubricating oil entering the back-pressure chamber 5 is partly guided from the compression chamber 9 into the back-pressure chamber 5 by the back-pressure hole 403, and partly guided from the first oil passage 17 and the second oil passage 18 into the back-pressure chamber 5. The compressed gas is discharged from the compression chamber 9 into the high-pressure chamber 15, then guided into the oil separation chamber 16 from the high-pressure chamber 15, and finally enters the back-pressure chamber 5 through the first oil passage 17 and the second oil passage 18.

[0051] As shown in Figure 2 The main bearing seat 2 has a gas guide passage 202 in communication with the suction chamber 14 and the compression chamber 9. The gas guide passage 202 is arranged to guide the refrigerant gas entering the suction chamber 14 into the compression chamber 9 for compression.

[0052] The above embodiments are only used to illustrate the present application and not to limit the technical solutions described in the present application. The understanding of the specification should be based on the skilled person in the art, for example, the directional descriptions such as "front", "back", "left", "right", "up", "down", etc. are only used to describe the relationship between objects, and are not essential limitations. "Multiple" means at least two or more.

[0053] Although the present application has been described in detail with reference to the above embodiments, it should be understood by those skilled in the art that the skilled person in the art can still modify or equivalently replace the present application, and all technical solutions and improvements within the spirit and scope of the present application should be covered within the scope of the claims of the present application.

Claims

1. A compressor, characterized in that, It includes a rotating shaft, a main bearing housing, a main bearing, a secondary bearing housing, and a secondary bearing. One end of the rotating shaft is fitted with the main bearing, and the main bearing is fixed to the main bearing housing. The other end of the rotating shaft is fitted with the secondary bearing, and the secondary bearing is fixed to the secondary bearing housing. The rotating shaft has a central oil passage and an auxiliary oil passage, the central oil passage is connected to the auxiliary oil passage, and the outlet of the auxiliary oil passage is opposite to the inner wall of the inner ring of the secondary bearing. The rotating shaft includes a connecting pin and a connecting end face. The connecting pin extends from the connecting end face away from the central oil passage and is eccentrically positioned relative to the axis of the rotating shaft. The center point of the projection of the connecting pin onto the connecting end face is on the same straight line as the center point of the connecting end face. The angle between the axial direction of the auxiliary oil passage and the straight line is defined as θ, where the range of θ is 0 < θ < 45°. The angle θ is oriented towards the side away from the connecting pin.

2. The compressor according to claim 1, characterized in that, The range of the angle θ between the axial direction of the auxiliary oil circuit and the straight line is: 0 < θ ≤ 10°.

3. The compressor according to claim 1, characterized in that, The compressor includes a moving scroll and has a back pressure chamber located between the moving scroll and the main bearing housing. The back pressure chamber is connected to the central oil circuit.

4. The compressor according to claim 3, characterized in that, The compressor includes a stationary scroll plate and a compression chamber located between the stationary scroll plate and the moving scroll plate. The moving scroll plate has a back pressure hole that connects the compression chamber and the back pressure chamber.

5. The compressor according to claim 3, characterized in that, The compressor includes an eccentric bushing having a socket, the connecting pin being at least partially located within the socket, and the eccentric bushing being fixed to the moving scroll.

6. The compressor according to claim 5, characterized in that, The eccentric bushing has a recessed opening located at the opening of the sleeve hole, and the recessed opening is opposite to the connecting end face; the recessed opening is at least partially opposite to the central oil passage, and the recessed opening is connected to the back pressure cavity.

7. The compressor according to claim 6, characterized in that, The end of the rotating shaft opposite the concave opening has a chamfer.

8. The compressor according to claim 4, characterized in that, The compressor includes a housing and an exhaust cover. In the axial direction of the main bearing housing, the housing and the exhaust cover are respectively connected to both ends of the main bearing housing. The compressor has an intake chamber located between the main bearing housing and the housing. The auxiliary bearing housing has a hole and a cavity, and the hole connects the intake chamber and the cavity.

9. The compressor according to claim 8, characterized in that, The compressor has a high-pressure chamber located between the stationary scroll and the exhaust cover, and the high-pressure chamber is connected to the compression chamber; the exhaust cover has an oil separation chamber connected to the high-pressure chamber; the exhaust cover has a first oil passage, and the main bearing housing has a second oil passage, the first oil passage is connected to the oil separation chamber, the first oil passage is connected to the second oil passage, and the second oil passage is connected to the back pressure chamber.

10. The compressor according to claim 8, characterized in that, The main bearing housing has an air guide channel, which connects the intake chamber and the compression chamber.

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