Compressor and air conditioner

Abstract

The present invention provides a compressor and an air conditioner, wherein the compressor comprises: a crankshaft, a rotor, a baffle, a main balancing block and a driving member, the crankshaft is arranged on the rotor, the ratio of the pressure at the exhaust port of the compressor to the pressure at the intake port of the compressor is a pressure ratio T, the baffle is arranged on the rotor, the main balancing block and the driving member are arranged on the baffle, and the driving member can drive the main balancing block to move on the baffle according to the size of the pressure ratio T. The defect in the prior art that the crankshaft rotor shaft system is unbalanced when the eccentric part of the crankshaft is subjected to a large gas pressure can be overcome.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a compressor and an air conditioner. Background Art

[0002] With the development of the industry, the evaporator and condenser of the air conditioner are currently developing towards miniaturization, which leads to the continuous increase in the operating frequency of the variable frequency rotor compressor, the increasingly severe working conditions, and the prominent vibration and noise problems of the compressor, which in turn leads to poor sound quality of the air conditioner. The balance level of the crankshaft rotor shaft system of the variable frequency rotor compressor has a significant impact on the vibration and noise of the compressor and the reliability of the shaft system parts. At present, the existing crankshaft rotor shaft system only balances the centrifugal force generated by the rotation of the eccentric part of the crankshaft by designing the main and auxiliary balance blocks on the upper and lower end surfaces of the rotor. See Figure 1 As shown, the main balance block 4 is designed on the opposite side of the crankshaft eccentric portion 9, and the auxiliary balance block 8 is designed on the same side of the crankshaft eccentric portion 9. However, the crankshaft rotor shaft system balance design method does not consider the influence of the gas pressure of the crankshaft eccentric portion. When the ratio of the exhaust pressure to the suction pressure of the compressor increases, Figure 2 As shown, when the working conditions are relatively severe, the gas pressure at the eccentric part of the crankshaft will be much greater than the centrifugal force at the eccentric part of the crankshaft, and the eccentric part of the crankshaft will be subjected to a larger gas pressure, resulting in an imbalance of the crankshaft rotor shaft system, wear of the compressor crankshaft, and aggravated vibration. Summary of the invention

[0003] Therefore, the present invention provides a compressor and an air conditioner, which can overcome the defect in the prior art that when the eccentric portion of the crankshaft is subjected to a large gas pressure, the crankshaft rotor shaft system will be unbalanced.

[0004] In order to solve the above problems, the present invention provides a compressor, comprising:

[0005] A crankshaft, a rotor, a baffle, a main balancing block and a driving member, wherein the crankshaft is arranged on the rotor, the ratio of the compressor exhaust port pressure to the compressor intake port pressure is the pressure ratio T, the baffle is arranged on the rotor, the main balancing block and the driving member are arranged on the baffle, and the driving member can drive the main balancing block to move on the baffle according to the size of the pressure ratio T.

[0006] In some embodiments, a guide rail is provided on the outer peripheral wall of the baffle along the circumference of the baffle, the guide rail passes through the outer peripheral wall of the baffle, the driving member is located on one side of the guide rail, the main balance block is located on the other side of the guide rail, and a connecting member is provided on the driving shaft of the driving member, and the connecting member passes through the guide rail and is connected to the main balance block.

[0007] In some embodiments, along a radial cross section of the baffle, the guide rail has a first end and a second end, with the center of the baffle as the center point, and an angle between the first end and the second end is 90°.

[0008] In some embodiments, a threaded hole is provided on the surface of the main balancing block facing the guide rail, the threaded hole is located at the center of the surface of the main balancing block facing the guide rail, and the connecting member passes through the guide rail and is connected to the threaded hole.

[0009] In some embodiments, the baffle is disposed on the rotor via a plurality of bolts, and a first groove is disposed on a surface of the main balance block facing the rotor along a circumference of the main balance block, and the first groove is opposite to the bolts.

[0010] In some embodiments, the baffle is L-shaped, a sliding portion is provided on the surface of the baffle facing away from the rotor, a second groove is provided on the surface of the main balance block facing the rotor, the second groove is opposite to the movement path of the main balance block, the sliding portion is provided in the second groove, and the sliding portion can slide in the second groove as the main balance block moves.

[0011] In some embodiments, an axial cross-section of the sliding portion and an axial cross-section of the second groove are T-shaped, and the sliding portion is snap-fitted into the second groove.

[0012] In some embodiments, with the axis of the baffle as the center, the rotation direction of the rotor is opposite to the movement direction of the main balancing weight.

[0013] In some embodiments, an eccentric portion is provided on the crankshaft. When the main balancing block moves to a fixed position, the angle formed by the center plane of the eccentric portion passing through the axial center line of the crankshaft and the center plane of the main balancing block passing through the axial center line of the crankshaft is the fixed angle α of the main balancing block, which satisfies that the fixed angle α increases with the increase of the compression ratio T.

[0014] In some embodiments, the pressure ratio T and the fixed angle α satisfy: when T≤1.5, α=0; when 1.5<T≤2.5, 0<α≤60°; when T>2.5; 60°<α≤90°.

[0015] The present invention also provides an air conditioner, comprising the compressor described in any of the preceding items.

[0016] A compressor and an air conditioner provided by the present invention ensure that the driving member and the crankshaft do not interfere with each other during assembly. When the eccentric portion of the crankshaft is subjected to a large gas pressure or other conditions, resulting in an imbalance in the crankshaft rotor shaft system, the driving member can drive the main balancing block to move on the baffle, thereby increasing the component of the balancing block inertial force in the gas pressure direction, thereby balancing the gas pressure and reducing the wear and vibration of the crankshaft. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a structural schematic diagram of a crankshaft rotor shaft system in the prior art;

[0018] Figure 2 It is a curve diagram showing the relationship between the force on the eccentric part of the crankshaft and the pressure ratio in the prior art;

[0019] Figure 3 A schematic diagram of the structure of a compressor according to an embodiment of the present invention;

[0020] Figure 4 is a schematic structural diagram of a rotor in a compressor according to an embodiment of the present invention;

[0021] Figure 5 A schematic diagram of the structure of a baffle in a compressor according to an embodiment of the present invention;

[0022] Figure 6 It is a structural schematic diagram of a main balancing block in a compressor according to an embodiment of the present invention;

[0023] Figure 7 is an assembly diagram of a compressor according to an embodiment of the present invention;

[0024] Figure 8 A top view of a compressor according to an embodiment of the present invention;

[0025] Fig. 9 A partial cross-sectional view of a compressor according to an embodiment of the present invention;

[0026] Fig.10 This is a principle analysis diagram of a fixed angle in a compressor according to an embodiment of the present invention;

[0027] Fig.11 It is a comparison curve of the vibration improvement effect of the compressor according to the embodiment of the present invention.

[0028] The reference numerals are as follows:

[0029] 1. baffle; 2. driving member; 3. connecting member; 4. main balancing block; 5. guide rail; 6. first groove; 7. threaded hole; 8. auxiliary balancing block; 9. eccentric part; 10. rotor; 11. crankshaft; 12. controller; 13. liquid distributor; 14. pressure sensor; 15. upper cover assembly; 16. housing assembly; 17. stator; 18. pump body assembly; 19. lower cover; 20. sliding part; 21. second groove. DETAILED DESCRIPTION

[0030] See also Figure 1 and Figure 2 As shown, in the prior art, the main balance block 4 is designed on the opposite side of the crankshaft eccentric portion 9, and the auxiliary balance block 8 is designed on the same side of the crankshaft eccentric portion 9. However, the crankshaft rotor shaft system balance design method does not consider the influence of the gas pressure of the crankshaft eccentric portion. When the ratio of the exhaust and intake pressures of the compressor increases and the working conditions are relatively bad, the gas pressure of the crankshaft eccentric portion will be much greater than the centrifugal force of the crankshaft eccentric portion. The crankshaft eccentric portion will be subjected to a large gas pressure, resulting in an imbalance of the crankshaft rotor shaft system, wear of the compressor crankshaft, and aggravated vibration.

[0031] See also Figure 3-11 As shown, the present invention provides a compressor, comprising: a crankshaft 11, a rotor 10, a baffle 1, a main balancing block 4 and a driving member 2, wherein the crankshaft 11 is arranged on the rotor 10, the ratio of the compressor exhaust port pressure to the compressor intake port pressure is a pressure ratio T, the baffle 1 is arranged on the rotor 10, the main balancing block 4 and the driving member 2 are arranged on the baffle 1, and the driving member 2 can drive the main balancing block 4 to move on the baffle 1 according to the size of the pressure ratio T. In this technical solution, the compressor is composed of an upper cover assembly 15, a shell assembly 16, a stator 17, a pump body assembly 18 and a lower cover 19. The lower cover 19, the upper cover assembly 15 and the shell assembly 16 constitute the compressor shell. A liquid separator 13 is arranged outside the compressor. The stator 17 and the pump body assembly 18 are arranged in the shell. The stator 17 is sleeved on the outer periphery of the rotor 10. During assembly, it is ensured that the driving member 2 and the crankshaft do not interfere with each other. When the eccentric part of the crankshaft is subjected to a large gas pressure or other conditions, resulting in an imbalance of the crankshaft rotor shaft system, the driving member 2 can drive the main balancing block 4 to move on the baffle 1, so that the component of the balancing block inertia force in the gas pressure direction is increased, thereby balancing the gas pressure and reducing the wear and vibration of the crankshaft.

[0032] In some embodiments, see Figure 4 and Figure 5As shown, along the circumference of the baffle 1, a guide rail 5 is provided on the outer peripheral wall of the baffle 1, and the guide rail 5 passes through the outer peripheral wall of the baffle 1. The driving member 2 is located on one side of the guide rail 5, and the main balance block 4 is located on the other side of the guide rail 5. A connecting member 3 is provided on the driving shaft of the driving member 2, and the connecting member 3 is connected to the main balance block 4 after passing through the guide rail 5. In this technical solution, the driving member 2 and the connecting member 3 can be arranged in such a way that the driving member 2 is stationary, a rack is arranged on the connecting member 3, and a gear is arranged on the driving shaft of the driving member 2 to drive the connecting member 3 to move. Alternatively, a slide groove is arranged on the baffle 1, the driving member 2 is arranged in the slide groove, and gears are arranged on the upper and lower guide rails. When the driving shaft of the driving member 2 rotates, the connecting member 3 moves in the guide rail, thereby causing the driving member 2 to move in the slide groove. The connecting member 3 is preferably a stud with threads at both ends. The movement path of the main balance block 4 is limited by the guide rail 5. The driving member 2 drives the main balance block 4 to move through the connecting member 3. The connecting member 3 fixes the main balance block 4 and bears the centrifugal force of the main balance block 4.

[0033] In some embodiments, see Figure 8 As shown, along the radial cross section of the baffle 1, the guide rail 5 has a first end and a second end, with the center of the baffle 1 as the center point, and the angle between the first end and the second end is 90°. Specifically, with the axis of the baffle as the center, the rotation direction of the rotor 10 is opposite to the movement direction of the main balance block 4. In this technical solution, the first end is the position where the fixed angle α of the main balancing block 4 is 0°. When the fixed angle α is 0°, the main balancing block 4 is designed on the opposite side of the crankshaft eccentric portion 9, that is, the main balancing block 4 and the crankshaft eccentric portion 9 are arranged at 180°. The first end is the initial end of the movement of the main balancing block 4, and the second end is the terminal end of the movement of the main balancing block 4. The maximum rotation angle of the main balancing block 4 on the guide rail 5 is further limited. The angle between the first end and the second end is 90°, so that the main balancing block 4 does not conflict with the auxiliary balancing block under the premise of ensuring the balancing effect. When the angle between the first end and the second end is greater than 90°, the balancing effect part of the main balancing block 4 at the first end or the second end will conflict with the balancing effect of the auxiliary balancing block, causing the problem of compressor vibration and noise. The rotation direction of the rotor 10 is opposite to the movement direction of the main balancing block 4. The driving force received by the main balancing block 4 and the inertia of the rotation of the rotor 10 are offset, ensuring the accuracy of adjusting the movement of the main balancing block 4.

[0034] In some embodiments, see Figure 6As shown, there is a threaded hole 7 on the surface of the main balancing block 4 facing the guide rail 5, and the threaded hole 7 is located at the center of the surface of the main balancing block 4 facing the guide rail 5. The connecting member 3 passes through the guide rail 5 and is connected to the threaded hole 7. In this technical solution, the main balancing block 4 is connected to the connecting member 3 through the threaded hole 7, and the threaded hole 7 is located at the center of the surface of the main balancing block 4 facing the guide rail 5, so as to maximize the effect of the driving force and make the main balancing block 4 move stably.

[0035] In some embodiments, see Figure 6 and Figure 7 As shown, the baffle 1 is arranged on the rotor 10 by a plurality of bolts, and a first groove 6 is arranged on the surface of the main balancing block 4 facing the rotor 10 along the circumference of the main balancing block 4, and the first groove 6 is opposite to the bolt. In this technical solution, the baffle 1 is fixed to the rotor 10 by bolts, and the first groove 6 ensures that when the main balancing block 4 moves, the surface of the main balancing block 4 facing the rotor 10 does not interfere with the bolts, thereby affecting the movement of the main balancing block 4.

[0036] In some embodiments, see Fig. 9 As shown, the longitudinal section of the baffle 1 is L-shaped, and a sliding portion 20 is provided on the surface of the baffle 1 facing away from the rotor 10, and a second groove 21 is provided on the surface of the main balancing block 4 facing the rotor 10, and the second groove 21 is opposite to the movement path of the main balancing block 4. The sliding portion 20 is arranged in the second groove 21, and the sliding portion 20 can slide in the second groove 21 with the movement of the main balancing block 4. Specifically, the axial section of the sliding portion 20 and the axial section of the second groove 21 are T-shaped, and the sliding portion 20 is clamped in the second groove 21. In this technical solution, the baffle 1 includes two parts, one part is provided with a guide rail 5, the other part is provided with a sliding portion 20, and the other part is provided on the rotor end surface. The second groove and the sliding portion 20 further limit the movement path of the main balancing block 4, ensuring that the movement path of the main balancing block 4 will not be affected by the centrifugal force. The up and down direction and radius of the main balancing block 4 are constrained to ensure the stability of the main balancing block 4.

[0037] In some embodiments, the baffle 1 is located on one end of the rotor 10 facing the eccentric portion 9, and the crankshaft 11 passes through the baffle 1. Figure 3 and Fig.10As shown, the crankshaft 11 is provided with an eccentric portion 9. When the main balancing block 4 moves to a fixed position, the angle formed by the center plane of the eccentric portion 9 passing through the axial center line of the crankshaft 11 and the center plane of the main balancing block 4 passing through the axial center line of the crankshaft 11 is the fixed angle α of the main balancing block 4, which satisfies that the fixed angle α increases with the increase of the pressure ratio T. Specifically, the pressure ratio T and the fixed angle α satisfy that when T≤1.5, α=0; when 1.5<T≤2.5, 0<α≤60°; when T>2.5; 60°<α≤90°. In this technical solution, the fixed angle α increases with the increase of the pressure ratio T. When the pressure ratio T is in any of the above intervals, the driving member 2 drives the main balancing block 4 to rotate to any value within the corresponding fixed angle α. At this time, the main balancing block 4 rotates with the rotor to balance the gas pressure received by the eccentric part 9. The component force of the inertial force of the main balancing block 4 in the gas pressure direction also increases, so that the gas force under different pressure ratios can be balanced by adjusting the fixed angle α. Figure 3 As shown, pressure sensors 14 are installed at the exhaust port and the intake port of the compressor, and are connected to the controller 12 by a signal transmission line. The controller 12 receives the compressor intake and exhaust pressure signals, calculates the current pressure ratio through an automatic control program, determines the main balance block fixed angle α, and sends the main balance block 4 fixed angle signal to the driver 2, so that the driver 2 drives the main balance block 4 to move. The working mode of the compressor is: the pressure sensor 14 at the intake and exhaust port monitors the intake and exhaust pressure in real time and uploads it to the controller 12. The controller 12 calculates the main balance fixed angle α according to the pressure ratio, and sends the fixed angle α signal to the driver 2. The driver 2 drives the main balance block 4 to rotate on the rotor baffle 1 to the required fixed angle α. The fixed angle α of the main balance block 4 is the angle formed by the center plane of the eccentric part 9 of the crankshaft and the center plane of the main balance block (the surface formed by the center line of the eccentric part and the center line of the major and minor shafts). The fixed angle α increases, see Fig.10 As shown in the figure, Fg is the pressure direction of the gas on the eccentric part 9, and F is the inertia force of the main balancing block, that is, the resultant force of the radially inward centripetal force and the radially outward centrifugal force of the main balancing block 4. The resultant force is radially inward, and the reaction force of the resultant force is the inertia force F of the main balancing block, which increases with the fixed angle α. The component force of the inertia force F of the main balancing block in the direction of gas pressure also increases, so that the gas force under different pressure ratios can be balanced by adjusting the fixed angle α. Fig.11 As shown, compared with the compressor in the prior art, the vibration intensity of the compressor of the present invention is stably lower than that of the compressor in the prior art.

[0038] The present invention also provides an air conditioner, comprising the above-mentioned compressor.

[0039] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present invention. These improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A compressor, characterized in that: include: A crankshaft (11), a rotor (10), a baffle (1), a main balancing block (4) and a driving member (2), wherein the crankshaft (11) is arranged on the rotor (10), the ratio of the pressure at the exhaust port of the compressor to the pressure at the intake port of the compressor is a pressure ratio T, the baffle (1) is arranged on the rotor (10), the main balancing block (4) and the driving member (2) are arranged on the baffle (1), and the driving member (2) can drive the main balancing block (4) to move on the baffle (1) according to the size of the pressure ratio T.

2. The compressor according to claim 1, characterized in that: A guide rail (5) is provided on the outer peripheral wall of the baffle (1) along the circumference of the baffle (1), and the guide rail (5) passes through the outer peripheral wall of the baffle (1). The driving member (2) is located on one side of the guide rail (5), and the main balance block (4) is located on the other side of the guide rail (5). A connecting member (3) is provided on the driving shaft of the driving member (2), and the connecting member (3) passes through the guide rail (5) and is connected to the main balance block (4).

3. The compressor according to claim 2, characterized in that: Along the radial cross section of the baffle (1), the guide rail (5) has a first end and a second end, with the center of the circle of the baffle (1) as the center point, and the angle between the first end and the second end is 90°.

4. The compressor according to claim 2, characterized in that: A threaded hole (7) is provided on the surface of the main balancing block (4) facing the guide rail (5); the threaded hole (7) is located at the center of the surface of the main balancing block (4) facing the guide rail (5); and the connecting member (3) passes through the guide rail (5) and is connected to the threaded hole (7).

5. The compressor according to claim 1, characterized in that: The baffle (1) is arranged on the rotor (10) by means of a plurality of bolts, and a first groove (6) is arranged on a surface of the main balance block (4) facing the rotor (10) along the circumference of the main balance block (4), wherein the first groove (6) is opposite to the bolts.

6. The compressor according to claim 1, characterized in that: The longitudinal section of the baffle (1) is L-shaped. A sliding portion (20) is provided on the surface of the baffle (1) facing away from the rotor (10). A second groove (21) is provided on the surface of the main balancing block (4) facing the rotor (10). The second groove (21) is opposite to the movement path of the main balancing block (4). The sliding portion (20) is arranged in the second groove (21). The sliding portion (20) can slide in the second groove (21) as the main balancing block (4) moves.

7. The compressor according to claim 6, characterized in that: An axial cross section of the sliding portion and an axial cross section of the second groove are T-shaped, and the sliding portion is clamped in the second groove.

8. The compressor according to claim 1, characterized in that: With the axis of the baffle as the center, the rotation direction of the rotor (10) is opposite to the movement direction of the main balancing block (4).

9. The compressor according to claim 1, characterized in that: The crankshaft (11) is provided with an eccentric portion (9). When the main balancing block (4) moves to a fixed position, an angle formed by a center plane of the eccentric portion (9) passing through the axial center line of the crankshaft (11) and a center plane of the main balancing block (4) passing through the axial center line of the crankshaft (11) is a fixed angle α of the main balancing block (4), which satisfies that the fixed angle α increases as the pressure ratio T increases.

10. The compressor according to claim 9, characterized in that: The pressure ratio T and the fixed angle α satisfy that when T≤1.5, α=0; when 1.5<T≤2.5, 0<α≤60°; when T>2.5; 60°<α≤90°.

11. An air conditioner, characterized in that: A compressor comprising the compressor according to any one of claims 1 to 10.

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