Oiling structure for compressor and rotor type compressor

Abstract

The present invention discloses an oiling structure for a compressor and a rotor-type compressor, comprising an eccentric shaft; a main bearing inner hole is provided at the center of the main bearing, and the eccentric shaft is passed through the main bearing inner hole; an eccentric shaft center hole is provided at the center of the eccentric shaft, and an oil suction piece is installed in the eccentric shaft center hole; the oil suction piece is a spiral oil suction piece; a spiral oil groove is provided on the hole wall of the main bearing inner hole, and the spiral oil groove is provided along the axial direction of the main bearing inner hole; a radial oil hole is provided on the eccentric shaft, one end of the radial oil hole is connected with the eccentric shaft center hole, and the other end of the radial oil hole is connected with the main bearing inner hole; the end point of the spiral part of the oil suction piece is located above the radial oil hole; the spiral starting point of the spiral oil groove is located below the center of the radial oil hole; the present invention can ensure that the compressor has high cooling capacity when running at low frequency and low power when running at high frequency; and avoid the local heat generation of the main bearing when the compressor runs at high frequency, causing a sharp temperature rise and a shaft seizure failure.

Description

Technical Field

[0001] The present invention belongs to the technical field of air-conditioning compressors, and in particular relates to an oiling structure for a compressor and a rotor-type compressor. Background Art

[0002] The rolling rotor compressor rotates through the eccentric shaft driven by the motor. The eccentric rotor rotates closely against the inner wall of the cylinder, forming a crescent-shaped space with periodic changes in volume to complete the suction, compression and exhaust processes. Among them, the eccentric shaft plays the main component of transmitting power. There is a gap between it and the main bearing. In order to prevent wear, refrigeration oil is usually stored in the gap. When the compressor rotates at high speed, the worn parts heat up, which requires not only motor oil lubrication, but also sufficient refrigeration oil lubrication to take away the heat.

[0003] At present, in order to save energy and reduce consumption, the operating range of variable frequency compressors is constantly expanding; for low-frequency operation, the refueling capacity of the refrigeration oil is significantly weakened. The main bearing of the compressor is the farthest away from the oil pool at the bottom of the compressor housing. It is very important whether the oil level raised by the low-speed rotation of the oil absorption plate in the oil hole of the eccentric shaft can reach the load surface of the main bearing.

[0004] Due to the structural design problems of the oil supply channel from the oil pool to the main bearing surface in the existing compressor structure, when the compressor operates at high frequency, the heat cannot be removed in time, causing the local temperature to rise sharply, which is prone to shaft seizure failure; when the compressor operates at low frequency, the oil supply height of the oil hole inside the eccentric shaft is insufficient, the main bearing surface is insufficiently lubricated, and the power increases; at the same time, there is no refrigeration oil seal in the spiral oil groove of the main bearing, resulting in gas leakage, and the low-frequency volumetric efficiency of the compressor drops sharply. Summary of the Invention

[0005] In response to the technical problems existing in the prior art, the present invention provides an oiling structure for a compressor and a rotor-type compressor to solve the technical problems of insufficient oiling height during low-frequency operation of the existing compressor, which leads to power increase and gas leakage, and small oil circulation volume during high-frequency operation, which leads to main bearing seizure.

[0006] In order to achieve the above object, the technical solution adopted by the present invention is:

[0007] The present invention provides an oiling structure for a compressor, comprising an eccentric shaft, a main bearing and an oil absorption sheet; a main bearing inner hole is provided at the center of the main bearing, and the eccentric shaft is passed through the main bearing inner hole;

[0008] The eccentric shaft is provided with an eccentric shaft center hole at its center, and the oil absorption sheet is installed in the eccentric shaft center hole; the oil absorption sheet is a spiral oil absorption sheet; a spiral oil groove is provided on the hole wall of the main bearing inner hole, and the spiral oil groove is provided along the axial direction of the main bearing inner hole;

[0009] A radial oil hole is provided on the eccentric shaft, one end of the radial oil hole is connected to the center hole of the eccentric shaft, and the other end of the radial oil hole is connected to the inner hole of the main bearing; the end point of the spiral part of the oil absorption plate is located above the radial oil hole; the spiral starting point of the spiral oil groove is located below the center of the radial oil hole.

[0010] Furthermore, the ratio of the spiral lift s of the oil absorption plate to the spiral lift S of the spiral oil groove is 0.3-0.7.

[0011] Furthermore, the ratio of the cross-sectional area a of the spiral oil groove to the area A of the radial oil hole is 0.4-0.6.

[0012] Furthermore, the spiral direction of the oil absorption sheet is opposite to the spiral direction of the spiral oil groove.

[0013] Furthermore, the center hole of the eccentric shaft is a concentric stepped hole, and the eccentric center hole includes a mounting hole section and a lift hole section; the mounting hole section is arranged close to the eccentric portion of the eccentric shaft, and the lift hole section is arranged at the main shaft portion of the eccentric shaft;

[0014] The diameter of the mounting hole section is larger than the diameter of the lift hole section; the oil absorption sheet is installed in the mounting hole section; the radial oil hole is arranged on the hole wall of the mounting hole section and is arranged close to the eccentric part of the eccentric shaft.

[0015] Furthermore, the ratio of the diameter D of the mounting hole section to the diameter d of the lift hole section is 1.3-1.8.

[0016] Furthermore, the oil absorbing sheet is installed in the installation hole section by using interference fit.

[0017] Furthermore, the interference between the oil absorbing sheet and the mounting hole section is 0.1-0.3 mm.

[0018] Furthermore, the distance between the end point of the spiral portion of the oil absorbing sheet and the center of the radial oil hole is 2-10 mm.

[0019] The present invention also provides a rotor-type compressor, comprising the oiling structure for the compressor.

[0020] Compared with the prior art, the present invention has the following beneficial effects:

[0021] The present invention provides an oiling structure for a compressor and a rotor-type compressor, in which the end point of the spiral part of the oil suction plate is arranged above the radial oil hole, and the spiral starting point of the spiral oil groove is arranged below the center of the radial oil hole, thereby ensuring that when the compressor is running at a low frequency, the highest oil level of the pump body can meet the lubrication requirements of the main bearing, thereby avoiding compressor power increase and gas leakage; at the same time, it can ensure that the compressor has high cooling capacity when running at a low frequency and low power when running at a high frequency; and avoid the main bearing from locally generating large heat when the compressor is running at a high frequency, causing a rapid temperature rise and a shaft seizure fault.

[0022] Furthermore, the ratio of the spiral lift s of the oil suction plate to the spiral lift S of the spiral oil groove is set to 0.3-0.7. When the spiral lift S of the main bearing oil groove remains unchanged, as the ratio of the spiral lift s of the oil suction plate to the spiral lift S of the spiral oil groove increases, when the compressor operates at a low frequency of 10HZ, the highest position of the refrigeration oil level gradually rises. When the ratio of the spiral lift s of the oil suction plate to the spiral lift S of the spiral oil groove is between 0.3-0.7, it can meet the lubrication of the low-frequency main bearing; at the same time, when the compressor operates at a high frequency of 120HZ, the flow rate of the refrigeration oil increases with the increase of the ratio of the spiral lift s of the oil suction plate to the spiral lift S of the spiral oil groove to meet the lubrication of the main bearing. When the ratio is greater than 0.7, the oil discharge volume of the compressor increases sharply and the height of the oil pool at the bottom of the compressor decreases.

[0023] Furthermore, the ratio of the cross-sectional area a of the spiral oil groove to the area A of the radial oil hole is set to 0.4-0.6. When the area A of the radial oil hole remains unchanged, as the ratio increases, during low-frequency 10HZ operation, the highest position of the refrigeration oil level gradually decreases until there is no refrigeration oil seal in the spiral oil groove of the main bearing, resulting in gas leakage and a sharp drop in the low-frequency volumetric efficiency of the compressor. When the ratio is between 0.4-0.6, it can ensure that there is oil in the main bearing oil groove and sealing is performed.

[0024] Furthermore, the ratio of the diameter D of the mounting hole section to the diameter d of the lift hole section is set to 1.3-1.8. As the ratio increases, the highest position of the refrigeration oil level gradually rises. When the ratio is 1.3-1.8, it can balance the main bearing lubrication and oil tank sealing of 10HZ low-frequency operation and the problem of large oil discharge of the compressor during 120HZ high-frequency operation.

[0025] Furthermore, the oil absorbing sheet is installed in the installation hole section by using interference fit, which ensures that there is no relative movement between the oil absorbing sheet and the eccentric shaft, thereby achieving synchronous rotation of the eccentric shaft and the oil absorbing sheet.

[0026] Furthermore, the interference between the oil absorption piece and the mounting hole is 0.1 to 0.3 mm. When the interference is large, the mounting hole is prone to generate burrs during the installation of the oil absorption piece, which will fall off under the high-speed impact of the refrigeration oil, be brought into the pump body, stay in the fitting clearance of the rotating parts, block the movement, and cause a malfunction. When the interference is small, the oil absorption piece and the eccentric shaft mounting hole will produce relative movement under the impact of the refrigeration oil, making the oiling function of the oil absorption piece ineffective.

[0027] Furthermore, when the distance between the end point of the spiral part of the oil absorption plate and the center of the radial oil hole is set to 2-10 mm, when the distance between the end point of the spiral part of the oil absorption plate and the center of the radial oil hole is set to less than 2 mm, the low-frequency 10HZ operation may easily cause discontinuity in the oil discharge of the radial oil hole. As the distance increases, the strength of the eccentric shaft and the internal and external oil pressures of the radial oil hole decrease. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 This is a schematic structural diagram of the oiling structure of the present invention;

[0029] Figure 2 Schematic diagram of the eccentric shaft structure in the present invention;

[0030] Figure 3 Schematic diagram of the main bearing structure in the present invention;

[0031] Figure 4 Schematic diagram of the partial structure of the spiral oil groove in the present invention;

[0032] Figure 5 It is a schematic structural diagram of the rotor compressor in the present invention.

[0033] Among them, 1 is the eccentric shaft, 2 is the main bearing, 3 is the oil suction plate, 4 is the compressor body, 5 is the oil reservoir; 101 is the main shaft part, 102 is the eccentric part, 103 is the eccentric shaft center hole, 104 is the radial oil hole; 1031 is the mounting hole section, 1032 is the lift hole section; 201 is the spiral oil groove; 301 is the end point of the spiral part of the oil suction plate. DETAILED DESCRIPTION

[0034] In order to make the technical problems, technical solutions and beneficial effects solved by the present invention more clearly understood, the present invention is further described in detail in the following specific embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0035] As attached Figure 1-4As shown, the present invention provides an oiling structure for a compressor, comprising an eccentric shaft 1, a main bearing 2 and an oil suction plate 3; the eccentric shaft 1 comprises a main shaft portion 101 and an eccentric portion 102; a main bearing inner hole is provided at the center of the main bearing 2, and the eccentric shaft 1 is inserted into the main bearing inner hole; wherein, the main bearing 2 is sleeved on the main shaft portion 101; an eccentric shaft center hole 103 is provided at the center of the eccentric shaft 1, and the oil suction hole 3 is installed in the eccentric shaft center hole 103.

[0036] In the present invention, the eccentric shaft center hole 103 is a concentric stepped hole; the eccentric center hole 103 includes a mounting hole section 1031 and a lift hole section 1032, the mounting hole section 1031 is arranged close to the eccentric portion 102 of the eccentric shaft 1, and the lift hole section 1032 is arranged at the main shaft portion 101 of the eccentric shaft 1; preferably, the ratio of the diameter D of the mounting hole section 1031 to the diameter d of the lift hole section 1032 is 1.3-1.8; as the ratio increases, the highest position of the rising oil level of the refrigerator gradually increases, and when the ratio is 1.3-1.8, it can balance the main bearing lubrication and oil tank sealing of 10HZ low-frequency operation and the problem of large oil discharge of the compressor during 120HZ high-frequency operation.

[0037] The oil absorbing sheet 3 is installed in the mounting hole section 1031. Preferably, the oil absorbing sheet 3 is installed in the mounting hole section 1032 using an interference fit, ensuring that the oil absorbing sheet and the eccentric shaft do not move relative to each other, thereby achieving synchronous rotation of the eccentric shaft and the oil absorbing sheet. Preferably, the interference fit between the oil absorbing sheet 3 and the mounting hole section 1032 is 0.1-0.3mm. If the interference fit is large, burrs are easily generated on the mounting hole during installation of the oil absorbing sheet. These burrs may fall off under the high-speed impact of the refrigeration oil, be carried into the pump body, and lodge in the clearance of the rotating components, blocking the movement and causing malfunction. If the interference fit is small, the oil absorbing sheet and the eccentric shaft mounting hole may move relative to each other under the impact of the refrigeration oil, rendering the oil absorbing sheet's oiling function ineffective.

[0038] A radial oil hole 104 is provided on the eccentric shaft 1. The radial oil hole 104 is located on the hole wall of the mounting hole section 1031 and is provided close to the eccentric portion 102 of the eccentric shaft 1. One end of the radial oil hole 104 is connected to the eccentric shaft center hole 103, and the other end is connected to the inner hole of the main bearing.

[0039] In the present invention, a spiral oil groove 201 is provided on the wall of the inner hole of the main bearing, and the spiral oil groove 201 is provided along the axial direction of the inner hole of the main bearing; the oil absorbing sheet 3 is a spiral oil absorbing sheet; the end point 301 of the spiral part of the oil absorbing sheet 3 is provided near one end of the lift hole section 1032, and the end point 301 of the spiral part is located above the radial oil hole; preferably, the distance between the end point 301 of the spiral part of the oil absorbing sheet 3 and the center of the radial oil hole 104 is 2-10 mm; the spiral end point of the oil absorbing sheet When the distance between the point and the center of the radial oil hole is set to be less than 2mm, the low frequency 10HZ operation is prone to discontinuity in the oil discharge of the radial oil hole. As the distance increases, the strength of the eccentric shaft and the internal and external oil pressures of the radial oil hole decrease; the spiral starting point of the spiral oil groove 201 is set close to the lower end surface of the main bearing 2, and the spiral starting point of the spiral oil groove 201 is located below the center of the radial oil hole 104; preferably, the distance between the spiral starting point of the spiral oil groove 201 and the center of the radial oil hole 104 is 1-3mm.

[0040] In this embodiment, the spiral direction of the oil absorption plate 3 is opposite to the spiral direction of the spiral oil groove 201; the ratio of the spiral lift s of the oil absorption plate 3 to the spiral lift S of the spiral oil groove 201 is 0.3-0.7; when the spiral lift S of the main bearing oil groove remains unchanged, as the ratio of the spiral lift s of the oil absorption plate to the spiral lift S of the spiral oil groove increases, when the compressor operates at a low frequency of 10HZ, the highest position of the refrigeration oil level gradually rises. When the ratio of the spiral lift s of the oil absorption plate to the spiral lift S of the spiral oil groove is between 0.3-0.7, it can meet the lubrication of the low-frequency main bearing; at the same time, when the compressor operates at a high frequency of 120HZ, the flow rate of the refrigeration oil increases with the increase of the ratio of the spiral lift s of the oil absorption plate to the spiral lift S of the spiral oil groove to meet the lubrication of the main bearing. When the ratio is greater than 0.7, the oil discharge volume of the compressor increases sharply and the height of the oil pool at the bottom of the compressor decreases.

[0041] The ratio of the cross-sectional area a of the spiral oil groove 201 to the area A of the radial oil hole 104 is 0.4-0.6; when the radial oil hole area A remains unchanged, as the ratio increases, during low-frequency 10HZ operation, the highest position of the refrigeration oil level gradually decreases until there is no refrigeration oil seal in the spiral oil groove of the main bearing, resulting in gas leakage and a sharp drop in the low-frequency volumetric efficiency of the compressor; when the ratio is between 0.4-0.6, it can ensure that there is oil in the main bearing oil groove and sealing is performed.

[0042] As attached Figure 5As shown, the present invention also provides a rotor-type compressor, including a compressor body 4 and an oil reservoir 5; the compressor body 4 includes the oiling structure for the compressor; in the rotor-type compressor, the main bearing is installed in the bearing hole of the main bearing seat, and the auxiliary bearing is installed in the bearing hole of the auxiliary bearing seat; the bottom of the shell of the compressor body 4 is the oil pool part of the compressor, and the oil pool part of the compressor is filled with a preset volume of refrigeration oil. When the compressor is running, the lowest oil level of the refrigeration oil is not lower than the lower end surface of the auxiliary bearing seat; the tail of the main bearing is installed with a motor rotor through a hot pressing process, and the main bearing on the eccentric shaft rotates under the drive of the motor, driving the eccentric rotor to rotate closely against the inner wall of the cylinder, and the sliding vane divides the crescent-shaped space into a low-pressure side and a high-pressure side. As the rotor rolls, the volume of the high and low-pressure crescent spaces changes periodically, and each rotation completes an intake and compression and exhaust process at the same time.

[0043] The oiling structure for a compressor and a rotor-type compressor described in the present invention are as follows: the center of the main bearing is provided with a main bearing inner hole, and the hole wall of the main bearing inner hole is provided with a longitudinal spiral oil groove; the center of the eccentric shaft is provided with an eccentric shaft center hole, and the eccentric shaft center hole is a concentric stepped hole, including a mounting hole section and a lift hole section; wherein the mounting hole section and the lift hole section are concentrically arranged and are through-set at the bottom of the mounting hole section; the oil suction piece is installed in the mounting hole section by an interference fit; the eccentric shaft is provided with a radial oil hole, and the radial oil hole is close to the eccentric part of the eccentric shaft; one end of the radial oil hole is connected with the eccentric shaft center hole, and the other end is connected with the main bearing inner hole; during the rotation of the compressor, the oiling structure is provided to mainly provide lubrication oil supply to the main bearing inner hole and end face; the oiling structure described in the present invention is suitable for a rolling rotor type variable frequency compressor, which can effectively reduce the friction power consumption of the main bearing when the compressor is running at high frequency; at the same time, it can effectively increase the oil level height of the refrigeration oil in the oil suction hole when the compressor is running at low frequency;

[0044] Working principle:

[0045] The oiling structure for the compressor described in the present invention is achieved by arranging an oil absorption sheet in the center hole of the eccentric shaft. Under the drive of the motor, the oil absorption sheet rotates, thereby transporting the refrigeration oil at the bottom of the compressor housing from the bottom upward to the radial oil hole to flow out. The refrigeration oil then gradually climbs along the spiral oil groove inside the main bearing hole until it reaches the top of the main bearing, thereby completing the lubrication of the entire main bearing hole surface.

[0046] In the present invention, the oil absorption plate and the center hole of the eccentric shaft are fitted with an interference fit without relative movement, thereby realizing synchronous rotation of the oil absorption plate when the main shaft rotates; the oil groove profiles of the oil absorption plate and the spiral oil groove are both spiral structures, and the rotation directions of the two spiral structures are opposite; after the oil absorption plate is installed, the end point of the spiral portion of the oil absorption plate is 2 to 10 mm higher than the center position of the radial oil hole; after the main shaft portion of the eccentric shaft and the main bearing are installed, the starting point height of the spiral oil groove in the inner hole of the main bearing is 1 to 3 mm lower than the center position of the radial oil hole.

[0047] In the present invention, the flow area ratio of the oil circuit in the eccentric shaft, the main bearing and the oil absorption plate is clarified, and the relative position of the interface part of each section of the oil circuit is specifically defined, which can well solve the full-band oiling efficiency of the vertical rolling rotor compressor and ensure the farthest position from the oil pool; at the same time, it realizes the lubrication of the compressor power output main bearing; under the current situation that the operating range of the variable frequency compressor is continuously widened, when the low frequency 10HZ operation is carried out, it can ensure that the oil level of the refrigerator oil reaches the main bearing, and effectively seal the refrigerant leakage through the oil tank; when the high frequency 120HZ operation is carried out, it can timely take away the friction heat of the main bearing, reduce the temperature of the main bearing, and at the same time establish a sufficient main shaft oil level to ensure reliable lubrication; it is suitable for variable frequency vertical rotor compressors with R32 / R410a as the working fluid.

[0048] When the main shaft of the eccentric shaft rotates driven by the motor, the oil absorption sheet penetrates into the oil pool to disturb the oil. The refrigeration oil spirals up along the surface of the oil absorption sheet in the center hole of the eccentric shaft and reaches the radial oil hole on the main bearing for discharge. When the end point of the spiral part of the oil absorption sheet is 2 to 10 mm higher than the center of the radial oil hole, the oil supply to the center hole is continuous and stable at a lower speed.

[0049] The spiral oil groove is a spiral groove structure with a preset depth set on the wall surface of the inner hole of the main bearing. Taking the 35-mounted variable frequency compressor for R32 working fluid as an example, when the compressor operates at the rated heating condition of 80HZ, the power consumption is reduced by 5 to 15W; when operating at the intermediate cooling condition of 10HZ, the cooling capacity is increased by 4 to 8W.

[0050] In the present invention, when the starting position of the spiral oil groove is 1 to 3 mm lower than the center of the radial oil hole, it is ensured that the refrigeration oil flowing out of the radial oil hole can directly flow into the spiral oil groove and rise along the oil groove to the top of the main bearing; the refrigeration oil flowing in the spiral oil groove, on the one hand, forms an oil film in the gap between the main bearing and the bearing seat to reduce the friction coefficient between the two, and on the other hand, promptly takes away the heat generated by the relative movement between the two.

[0051] The oiling structure for a compressor and a rotor-type compressor described in the present invention optimize the oil circuit structure and parameters from the oil pool to the main bearing, and at the same time, determine the relative relationship between the end point of the spiral portion of the oil suction plate and the radial oil hole, as well as the relative relationship between the radial oil hole and the starting point of the spiral oil groove, thereby ensuring effective oiling of the vertical rolling rotor compressor in the full frequency band; the main bearing is the component farthest from the oil pool at the bottom of the shell in the vertical compressor, and is also the component for the power output of the compressor. Its effective lubrication is very important to the reliability of the compressor; the oil circuit parameters determined by the present invention can ensure that the compressor has high cooling capacity in low-frequency operation and low power in high-frequency operation during full-frequency operation; the present invention is suitable for variable-frequency compressors using R32 / R410a as the refrigerant, and avoids large local heating of the main bearing during high-frequency operation, which causes a sharp temperature rise and shaft seizure failure.

[0052] The above embodiment is only one of the implementation methods that can realize the technical solution of the present invention. The scope of protection claimed by the present invention is not limited only to this embodiment, but also includes changes, replacements and other implementation methods that can be easily thought of by any technician familiar with this technical field within the technical scope disclosed by the present invention.

Claims

1. A lubricating structure for a compressor, characterized in that: It comprises an eccentric shaft (1), a main bearing (2) and an oil absorption sheet (3); a main bearing inner hole is provided at the center of the main bearing (2), and the eccentric shaft (1) is inserted into the main bearing inner hole; An eccentric shaft center hole (103) is provided at the center of the eccentric shaft (1), and the oil absorption sheet (3) is installed in the eccentric shaft center hole (103); the oil absorption sheet (3) is a spiral oil absorption sheet; a spiral oil groove (201) is provided on the hole wall of the main bearing inner hole, and the spiral oil groove (201) is provided along the axial direction of the main bearing inner hole; The eccentric shaft (1) is provided with a radial oil hole (104), one end of the radial oil hole (104) is communicated with the central hole (103) of the eccentric shaft, and the other end of the radial oil hole (104) is communicated with the inner hole of the main bearing; the end point (301) of the spiral portion of the oil absorbing sheet (3) is located above the radial oil hole (104); the spiral starting point of the spiral oil groove (201) is located below the center of the radial oil hole (104); The ratio of the spiral lift s of the oil absorption plate (3) to the spiral lift S of the spiral oil groove (201) is 0.3-0.7; The ratio of the cross-sectional area a of the spiral oil groove (201) to the area A of the radial oil hole (104) is 0.4-0.

6.

2. The oiling structure for a compressor according to claim 1, characterized in that: The spiral direction of the oil absorption sheet (3) is opposite to the spiral direction of the spiral oil groove (201).

3. The oiling structure for a compressor according to claim 1, characterized in that: The eccentric shaft center hole (103) is a concentric stepped hole, and the eccentric shaft center hole (103) includes a mounting hole section (1031) and a lift hole section (1032); the mounting hole section (1031) is arranged close to the eccentric portion (102) of the eccentric shaft (1), and the lift hole section (1032) is arranged on the main shaft portion (101) of the eccentric shaft (1); The diameter of the mounting hole section (1031) is larger than the diameter of the lift hole section (1032); the oil absorption sheet (3) is installed in the mounting hole section (1031); and the radial oil hole (104) is arranged on the hole wall of the mounting hole section (1031) and is arranged close to the eccentric portion (102) of the eccentric shaft (1).

4. The oiling structure for a compressor according to claim 3, characterized in that: The ratio of the diameter D of the installation hole section (1031) to the diameter d of the lift hole section (1032) is 1.3-1.

8.

5. The oiling structure for a compressor according to claim 3, characterized in that: The oil absorbing sheet (3) is installed in the installation hole section (1032) by means of interference fit.

6. The oiling structure for a compressor according to claim 5, characterized in that: The interference between the oil absorbing sheet (3) and the mounting hole section (1032) is 0.1-0.3 mm.

7. The oiling structure for a compressor according to claim 1, characterized in that: The distance between the end point (301) of the spiral portion of the oil absorbing sheet (3) and the center of the radial oil hole (104) is 2-10 mm.

8. A rotary compressor, characterized in that: The invention comprises an oiling structure for a compressor as described in any one of claims 1 to 7.

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