Scroll compressor and vehicle

Abstract

The scroll compressor comprises a crankshaft, a motor, an eccentric sleeve, a movable scroll plate, a main bearing, a shaft balance block and a balancing weight, the crankshaft comprises a main body part and an eccentric part, the motor drives the crankshaft to rotate, the eccentric sleeve is in clearance fit with the eccentric part, the shaft balance block and the eccentric sleeve are mutually independent, and the main bearing is arranged on the main body part. A gap is formed between the shaft balance block and the eccentric sleeve, and the balance weight block is connected to the axial end of the motor. According to the scroll compressor, the vibration of the eccentric sleeve cannot be transmitted to the shaft balance block, and the shaft balance block is prevented from vibrating along with the eccentric sleeve and deviating in angle, so that the noise and the vibration during operation of the scroll compressor are reduced, the stability of the dynamic balance of a shaft system of the scroll compressor is improved, and the distance between the shaft balance block and the dynamic scroll plate is reduced; and the distance between the shaft balance block and the main bearing is increased, and the mass of the shaft balance block and the balancing weight for dynamic balance is reduced, so that the overall weight of the scroll compressor is reduced.

Description

TECHNICAL FIELD

[0001] The utility model relates to scroll compressor technical field especially relates to a scroll compressor and vehicle. BACKGROUND

[0002] In scroll compressor, the crankshaft is connected with the eccentric weight sleeve through the eccentric pin, the eccentric weight sleeve is connected with the orbiting scroll through the bearing, the rotation power of the crankshaft is transmitted to the orbiting scroll, and the eccentric mass of the eccentric pin and the bearing is balanced, since the eccentric weight sleeve rotates along with the eccentric pin, the eccentric weight sleeve needs to be matched with the eccentric pin, when the crankshaft rotates at high speed, the gap between the eccentric weight sleeve and the eccentric pin causes the vibration and angle deviation of the eccentric weight sleeve, which further destroys the shafting dynamic balance of the scroll compressor and increases the vibration and noise of the whole scroll compressor, and the method of moving the weight part of the eccentric weight sleeve away from the orbiting scroll to reduce the vibration needs to increase the weight of the weight part to realize the shafting dynamic balance, which increases the weight of the whole scroll compressor. SUMMARY

[0003] The utility model aims at solving one of the technical problems in the prior art at least, for this purpose, the utility model provides a scroll compressor, which can improve the stability of the shafting dynamic balance of the scroll compressor, reduce the noise and vibration during operation of the scroll compressor, and reduce the weight of the whole scroll compressor.

[0004] The utility model further provides a vehicle with the scroll compressor.

[0005] The scroll compressor according to the first aspect of the utility model comprises:

[0006] The crankshaft comprises a main body part and an eccentric part connected to one end of the main body part, and the axis of the eccentric part is eccentric relative to the axis of the main body part;

[0007] The motor is connected to the main body part and is used to drive the rotation of the crankshaft;

[0008] The eccentric sleeve is sleeved on the outside of the eccentric part and is matched with the eccentric part in a gap;

[0009] The orbiting scroll is drivingly connected with the eccentric sleeve through the orbiting bearing and rotates along with the eccentric part;

[0010] The main bearing is sleeved on the outside of the main body part, and along the axial direction of the crankshaft, the main bearing is located between the motor and the orbiting scroll;

[0011] A shaft balance block is fixed to the main body part, and the shaft balance block is located on the side of the main bearing facing the orbiting scroll, the shaft balance block is independent of the eccentric sleeve, and a gap is formed between the shaft balance block and the eccentric sleeve.

[0012] A counterweight is connected to the end of the motor shaft.

[0013] The scroll compressor has at least the following beneficial effects:

[0014] In the utility model, the shaft balance block is fixed to the main body part, the eccentric sleeve and the shaft balance block are independent of each other, and a gap is formed between the eccentric sleeve and the shaft balance block; when the motor drives the crankshaft to rotate at a high speed, the vibration of the eccentric sleeve cannot be transmitted to the shaft balance block, the vibration and the angular deviation of the shaft balance block following the eccentric sleeve are prevented, the noise and the vibration of the scroll compressor during operation are reduced, the stability of the shafting dynamic balance of the scroll compressor is improved, in addition, the shaft balance block is located on the side of the main bearing facing the orbiting scroll, the distance between the shaft balance block and the orbiting scroll is reduced, the distance between the shaft balance block and the main bearing is increased, the force arm of the shaft balance block is increased, the balance torque that can be provided by the shaft balance block during rotation is increased, and the mass of the shaft balance block and the counterweight used for dynamic balancing is reduced, and thus the overall weight of the scroll compressor is reduced.

[0015] According to some embodiments of the utility model, a part of the shaft balance blocks are located between the main bearing and the orbiting bearing.

[0016] And / or, the shaft balance block comprises a first balance part and a second balance part connected to the circumferential side of the first balance part, at least a part of the second balance part is arranged protruding away from the main bearing compared with the first balance part.

[0017] According to some embodiments of the utility model, the shaft balance block and the eccentric sleeve are arranged adjacent along the axial direction of the crankshaft, and a part of the shaft balance blocks are arranged around the outer periphery of the eccentric sleeve.

[0018] According to some embodiments of the utility model, the orbiting scroll comprises a bottom plate and a mounting wall connected to the side of the bottom plate facing the main bearing, a part of the orbiting bearings are installed inside the mounting wall, and a part of the shaft balance blocks are arranged around the outer periphery of the mounting wall.

[0019] According to some embodiments of the utility model, the mounting wall has a first mounting part and a second mounting part connected along the axial direction of the orbiting scroll, the thickness of the first mounting part along the radial direction of the orbiting scroll is greater than the thickness of the second mounting part along the radial direction of the orbiting scroll.

[0020] According to some embodiments of the present application, the shaft balance block is sleeved on the outside of the main body part and is in interference fit with the main body part.

[0021] According to some embodiments of the present application, the eccentric sleeve comprises a first connecting part and a second connecting part, the second connecting part is located at one end of the first connecting part and is connected to the circumferential side of the first connecting part, the orbiting bearing is sleeved on the outside of the first connecting part, and the second connecting part is abutted to the end of the main body part and the inner ring of the orbiting bearing respectively on the two axially opposite sides.

[0022] According to some embodiments of the present application, the eccentric part is inserted and fixed at one end of the main body part.

[0023] According to some embodiments of the present application, a plurality of counterweights are arranged, and at least one of the counterweights is connected to the end of the motor away from the orbiting scroll.

[0024] Alternatively, one counterweight is arranged and connected to the end of the motor away from the orbiting scroll.

[0025] The vehicle according to the second aspect embodiment of the present application comprises the scroll compressor according to the first aspect embodiment.

[0026] Additional aspects and advantages of the present application will be given in part in the following description, will become apparent from the following description, or will be learned by practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0027] The present application will be further described below in combination with the drawings and embodiments, in which:

[0028] Figure 1 is a sectional view of an embodiment of the shaft dynamic balance related structure in the scroll compressor of the present application;

[0029] Figure 2 is a sectional view of Figure 1 ;

[0030] Figure 3 is a sectional view of an embodiment of the scroll compressor of the present application;

[0031] Figure 4 is a sectional view of Figure 2 ;

[0032] Figure 5 is a schematic view of an embodiment of the shaft balance block;

[0033] Figure 6 is a schematic view of an embodiment of the orbiting scroll;

[0034] Figure 7 Schematic view of one embodiment of eccentric sleeve.

[0035] Reference signs:

[0036] Shaft balance block 10, first balance part 11, second balance part 12; counterweight 20; crankshaft 100, main body part 110, eccentric part 120; motor 200, rotor 210; moving scroll 300, bottom plate 310, anti-rotation hole 311, weight-reducing hole 312, scroll tooth 320, mounting wall 330, first mounting part 331, second mounting part 332, mounting hole 340; static scroll 400; eccentric sleeve 500, first connecting part 510, through hole 511, second connecting part 520; moving disc bearing 600; main bearing 700; bearing seat 800, first mounting cavity 810, second mounting cavity 820, anti-rotation pin 830; housing 900. DETAILED DESCRIPTION

[0037] The embodiments of the present application are described in detail below, examples of which are shown in the drawings, wherein the same or similar notations represent the same or similar elements having the same or similar functions throughout. The embodiments described below by reference to the drawings are exemplary only, and are used only for explaining the present application, and cannot be understood as a limitation of the present application.

[0038] In the description of the present application, it should be understood that the orientation description, such as the orientation or position relationship indicated by up, down, front, back, left, right, etc. is based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as a limitation of the present application.

[0039] In the description of the present application, the meaning of several is more than one, the meaning of multiple is more than two, greater than, less than, more than, etc. are understood as not including the number, above, below, etc. are understood as including the number. If it is described as first, second, it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features or the sequence of indicated technical features.

[0040] In the description of the present application, unless otherwise explicitly limited, the words such as setting, mounting, connecting, etc. should be understood in a broad sense, and the person skilled in the art can reasonably determine the specific meaning of the above words in the present application in combination with the specific content of the technical solution.

[0041] In the description of the present utility model, the description of the reference terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example" or "some examples" means that the specific features, structures, materials or characteristics described in combination with the embodiment or example are included in at least one embodiment or example of the present utility model. In the present specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0042] The scroll compressor comprises a dynamic scroll disc and a static scroll disc with the same involute profile and a phase difference of 180°, the dynamic scroll disc rotates around the static scroll disc with a certain eccentricity, the static scroll disc is fixed on a rack, and the mutual revolution of the dynamic scroll disc and the static scroll disc forms continuous change of a closed volume, so as to realize the purpose of compressing gas. Generally, the eccentric rotation of the dynamic scroll disc is realized by the following mode, i.e. the crankshaft is connected with the eccentric weight sleeve through the eccentric pin, the eccentric weight sleeve is connected with the dynamic scroll disc through the dynamic disc bearing, the rotating power is transmitted from the crankshaft to the dynamic scroll disc, and the eccentric mass of the eccentric pin and the dynamic disc bearing is balanced; however, in order to make the eccentric weight sleeve rotate circumferentially with the eccentric pin, the eccentric weight sleeve needs to be matched with the eccentric pin in clearance, when the crankshaft rotates at high speed, the clearance between the eccentric weight sleeve and the eccentric pin causes the eccentric weight sleeve to vibrate and deviate in angle, thereby damaging the shaft dynamic balance of the scroll compressor and increasing the vibration and noise of the whole scroll compressor, when the scroll compressor is applied to the air conditioning system of a vehicle, the NVH performance of the whole vehicle will be affected. The mode of reducing vibration by moving the weight part in the eccentric weight sleeve away from the dynamic scroll disc needs to increase the energy of the weight part to maintain the shaft dynamic balance of the scroll compressor, so that the weight of the whole scroll compressor is increased.

[0043] Based on the above, in the embodiment of the present utility model, a scroll compressor is provided with reference to Figures 1 to 3The scroll compressor comprises a crankshaft 100, a motor 200 and a moving scroll 300. The crankshaft 100 comprises a main body 110 and an eccentric part 120 connected to one end of the main body 110. The axis of the main body 110 is parallel to the axis of the eccentric part 120. The eccentric part 120 is eccentrically arranged relative to the axis of the main body 110. The motor 200 is connected to the main body 110 and provides rotational power to the crankshaft 100 to drive the rotation of the crankshaft 100. When the main body 110 rotates around its own axis, the eccentric part 120 rotates around the axis of the main body 110 in a circular motion. The scroll compressor further comprises a stationary scroll 400. The moving scroll 300 is in transmission connection with the eccentric part 120. The stationary scroll 400 is in a fixed state. The scroll teeth of the moving scroll 300 are in meshing connection with the scroll teeth of the stationary scroll 400. The moving scroll 300 revolves around the axis of the stationary scroll 400 and continuously changes the closed volume to achieve the compression of gas.

[0044] The scroll compressor further comprises an eccentric sleeve 500. The eccentric sleeve 500 is sleeved on the outside of the eccentric part 120 and is in clearance fit with the eccentric part 120. When the eccentric part 120 rotates around the axis of the main body 110 in a circular motion, the eccentric sleeve 500 rotates with the eccentric part 120 and can rotate relative to the eccentric part 120. The scroll compressor further comprises a moving disc bearing 600 and a main bearing 700. The main bearing 700 is sleeved on the outside of the main body 110 and is located between the motor 200 and the moving scroll 300 along the axial direction of the crankshaft 100. The main body 110 is arranged in the inner ring of the main bearing 700. In some embodiments, the scroll compressor further comprises a bearing seat 800. The outer ring of the main bearing 700 is in fit with the bearing seat 800. The bearing seat 800 is fixed to the shell 900 of the scroll compressor. When the motor 200 drives the rotation of the main body 110, the inner ring and the outer ring of the main bearing 700 rotate relative to each other. The main bearing 700 supports the main body 110 to rotate stably. The moving disc bearing 600 is in transmission connection between the eccentric sleeve 500 and the moving scroll 300. The moving disc bearing 600 is used to transmit power from the eccentric sleeve 500 to the moving scroll 300 and make the moving scroll 300 revolve around the stationary scroll 400 relative to the rotation of the eccentric part 120.

[0045] The eccentric sleeve 500, the eccentric part 120, the orbiting scroll bearing 600 and the orbiting scroll 300 are all moving parts in the shaft system of the scroll compressor, and are all eccentrically arranged relative to the main body 110, and are all shaft system eccentric masses of the scroll compressor. The scroll compressor further comprises a shaft balance block 10 and a counterweight 20. The shaft balance block 10 is fixed to the main body 110 and can rotate synchronously with the main body 110. The counterweight 20 is connected to the end of the motor shaft 200. Specifically, the rotor 210 of the motor 200 is sleeved outside the main body 110 and drives the main body 110 to rotate synchronously. The counterweight 20 is connected to the end of the rotor 210 of the motor 200 and rotates synchronously with the rotor 210. The shaft balance block 10 and the counterweight 20 are used to balance the rotational inertia force and the rotational inertia moment of the orbiting scroll 300, the eccentric sleeve 500, the eccentric part 120 and the orbiting scroll bearing 600 in motion, so as to realize dynamic balance of the shaft system of the scroll compressor.

[0046] In the embodiment, the power transmission from the eccentric part 120 to the orbiting scroll 300 is realized by the gap cooperation between the eccentric sleeve 500 and the eccentric part 120, so that the orbiting scroll 300 revolves relative to the fixed scroll 400. Since the eccentric sleeve 500 and the shaft balance block 10 are independent of each other and there is a gap between the eccentric sleeve 500 and the shaft balance block 10, when the motor 200 drives the crankshaft 100 to rotate at a high speed, the shaft balance block 10 is fixed to the main body 110 and can rotate synchronously with the main body 110 to balance the rotational inertia force and the rotational inertia moment. In addition, the vibration of the eccentric sleeve 500 cannot be transmitted to the shaft balance block 10, which prevents the shaft balance block 10 from vibrating and angularly deviating with the eccentric sleeve 500, thereby reducing the noise and vibration of the scroll compressor during operation. When the scroll compressor is applied to the air conditioning system of a vehicle, the NVH performance of the vehicle can be improved. In addition, the scroll compressor can continuously maintain the balance of the rotational inertia force and the rotational inertia moment, thereby improving the stability of the dynamic balance of the shaft system of the scroll compressor.

[0047] In addition, the shaft balance block 10 is located on the side of the main bearing 700 facing the orbiting scroll 300, so as to reduce the distance between the shaft balance block 10 and the orbiting scroll 300 and increase the distance between the shaft balance block 10 and the main bearing 700. The force arm of the shaft balance block 10 is increased, so as to increase the balance moment that can be provided by the shaft balance block 10 when rotating. In addition, the mass of the shaft balance block 10 and the counterweight 20 used for dynamic balance can be reduced, thereby reducing the overall weight of the scroll compressor.

[0048] The dynamic balance of the shaft system of the scroll compressor can be measured by selecting any cross section of the main body 110 as a reference. In the embodiment, the end surface of the main bearing 700 facing the orbiting scroll 300 is taken as a reference to introduce the balance of the rotational inertia force and the rotational inertia moment of the scroll compressor.

[0049] Reference Figure 4F1 is the rotational inertial force of the counterweight 20, F2 is the rotational inertial force of the moving scroll plate 300, F3 is the rotational inertial force of the shaft balance block 10, F4 is the rotational inertial force of the eccentric part 120, F5 is the rotational inertial force of the eccentric sleeve 500, and F6 is the rotational inertial force of the moving disc bearing 600. M1 is the rotational inertial torque of the counterweight 20, M2 is the rotational inertial torque of the moving scroll plate 300, M3 is the rotational inertial torque of the shaft balance block 10, M4 is the rotational inertial torque of the eccentric part 120, M5 is the rotational inertial torque of the eccentric sleeve 500, and M6 is the rotational inertial torque of the moving disc bearing 600. All of the above inertial forces can be expressed by F = mrω. 2 The inertial torque can be calculated by M = F × L, where F is the rotational inertial force of the corresponding component, M is the rotational inertial torque of the corresponding component, ω is the angular velocity of the crankshaft 100 driven by the motor 200 (the angular velocities of the components are the same), r is the rotational radius of the component, m is the mass of the component, and L is the distance from the center of mass of the component to the end face of the main bearing 700 toward the moving scroll plate 300.

[0050] The cross-section formed by cutting the crankshaft 100 with a plane parallel to the axis of the crankshaft 100 is used as the reference plane (e.g. Figure 4 As shown, the counterweight 20 and the shaft balance block 10 are located on different sides of the reference plane, and the eccentric part 120, the eccentric sleeve 500, the moving disc bearing 600, and the moving scroll 300 are all eccentrically positioned on the same side of the reference plane as the counterweight 20. When the crankshaft 100 rotates, the rotational inertial torque generated by the moving scroll 300, the moving disc bearing 600, the eccentric sleeve 500, and the eccentric part 120 is counterclockwise, while the rotational inertial torque generated by the counterweight 20 and the shaft balance block 10 is clockwise. Therefore, the rotational inertial force balance of the scroll compressor shaft system must satisfy F3=F1+F2+F4+F5+F6, and the rotational inertial torque balance of the scroll compressor shaft system must satisfy M1+M3=M2+M4+M5+M6.

[0051] By matching the shaft balancing block 10 with the counterweight 20, the balance of the rotational inertia force and the rotational inertia moment of the scroll compressor shaft can be realized at the same time, so that the scroll compressor shaft remains dynamic balance. In addition, the shaft balancing block 10 and the counterweight 20 balance the rotational inertia force and the rotational inertia moment of the dynamic scroll plate 300, the dynamic plate bearing 600, the eccentric part 120 and the eccentric sleeve 500 together. According to the specific setting of the scroll compressor shaft, the mass of the shaft balancing block 10 and / or the counterweight 20 can be increased or decreased, or the position of the shaft balancing block 10 and / or the counterweight 20 can be moved to realize the dynamic balance of the shaft. The configuration of the dynamic balance of the shaft is more flexible. By increasing the distance between the center of mass of the shaft balancing block 10 and the end face of the main bearing 700, and / or the distance between the center of mass of the counterweight 20 and the end face of the main bearing 700, the mass of the shaft balancing block 10 and / or the counterweight 20 can be reduced, and the overall weight of the scroll compressor can be reduced.

[0052] The shaft balancing block 10 can be fixed to the main body part 110 by thread connection, casting, welding and the like, so that the shaft balancing block 10 can rotate synchronously with the main body part 110. In an embodiment, referring to Figure 2 With Figure 5 , the shaft balancing block 10 includes a first balancing part 11 and a second balancing part 12, the second balancing part 12 is connected to the circumferential side of the first balancing part 11, the first balancing part 11 is sleeved on the outside of the main body part 110, the first balancing part 11 and the main body part 110 are interference fit, the connection between the first balancing part 11 and the main body part 110 is more stable, and the assembly of the first balancing part 11 and the main body part 110 is more convenient, and the processing of the crankshaft 100 and the shaft balancing block 10 is facilitated.

[0053] Similarly, the counterweight 20 can be fixed to the end face of the rotor 210 of the motor 200 by thread connection, casting, welding and the like, so that the counterweight 20 can rotate synchronously with the rotor 210.

[0054] In an embodiment, the projection of the counterweight 20 along the axial direction of the crankshaft 100 is semicircular, and is arranged around the outside of the main body part 110. According to the dynamic balance requirement of the scroll compressor, the central angle of the counterweight 20, the width of the counterweight 20 along the radial direction of the crankshaft 100, the thickness of the counterweight 20 along the axial direction of the crankshaft 100, etc. can be increased or decreased. In an embodiment, the projection of the shaft balancing block 10 along the axial direction of the crankshaft 100 is similar to a sector. According to the dynamic balance requirement of the scroll compressor, the central angle of the shaft balancing block 10, the radius of the shaft balancing block 10, the thickness of the shaft balancing block 10 along the axial direction of the crankshaft 100, etc. can be increased or decreased.

[0055] At least part of the shaft balance block 10 is located between the main bearing 700 and the orbiting bearing 600, on the one hand, the shaft balance block 10 is as close to the orbiting scroll 300 as possible, the distance between the shaft balance block 10 and the orbiting scroll 300 is reduced, and on the other hand, the distance between the shaft balance block 10 and the main bearing 700 is increased, so as to increase the force arm generated by the rotation of the shaft balance block 10, thereby reducing the mass of the shaft balance block 10, and on the other hand, the shaft balance block 10 is separated from the vibration parts such as the eccentric sleeve 500, so as to reduce the noise and vibration of the scroll compressor during operation.

[0056] In order to further increase the rotation force arm of the shaft balance block 10 and reduce the mass of the shaft balance block 10, in an embodiment, referring to Figure 2 , at least part of the second balance part 12 is protruded away from the main bearing 700 compared with the first balance part 11, so that the center of mass of the shaft balance block 10 is further close to the orbiting scroll 300 and away from the main bearing 700, the distance between the center of mass of the shaft balance block 10 and the end face of the main bearing 700 is increased, and a shaft balance block 10 with smaller mass can meet the dynamic balance requirement of the shaft system of the scroll compressor, thereby reducing the overall weight of the scroll compressor.

[0057] In an embodiment, the shaft balance block 10 and the eccentric sleeve 500 are arranged adjacent to each other along the axial direction of the crankshaft 100, and the shaft balance block 10 and the eccentric sleeve 500 have a gap along the axial direction of the crankshaft 100, on the one hand, the shaft balance block 10 is as close to the orbiting scroll 300 as possible, the rotation force arm of the shaft balance block 10 is increased, and the mass of the shaft balance block 10 is reduced, on the other hand, the shaft balance block 10 and the eccentric sleeve 500 make full use of the space between the main bearing 700 and the orbiting bearing 600, so that the internal components of the scroll compressor are arranged more compactly, and the overall volume of the scroll compressor is reduced.

[0058] Further, referring to Figure 2 , part of the shaft balance block 10 is arranged around the outer periphery of the eccentric sleeve 500, and specifically, at least part of the second balance part 12 is arranged around the outer periphery of the eccentric sleeve 500, on the one hand, the first balance part 11 is lengthened, the second balance part 12 is arranged around the outer periphery of the eccentric sleeve 500, the radius of the shaft balance block 10 is increased, the shaft balance block 10 has a larger rotation radius, the rotation inertia moment that can be provided by the shaft balance block 10 is increased, and the weight of the shaft balance block 10 is reduced, on the other hand, the second balance part 12 is protruded away from the main bearing 700 and towards the orbiting scroll 300, and is arranged around the outer periphery of the eccentric sleeve 500, so that the center of mass of the shaft balance block 10 is further close to the orbiting scroll 300 and away from the main bearing 700, the distance between the center of mass of the shaft balance block 10 and the end face of the main bearing 700 is increased, and a shaft balance block 10 with smaller mass can meet the dynamic balance requirement of the shaft system of the scroll compressor, thereby reducing the overall weight of the scroll compressor.

[0059] Referring to Figure 2 With Figure 6 , the orbiting scroll plate 300 comprises a base plate 310, a scroll tooth 320 is arranged on the side of the base plate 310 away from the main bearing 700 and is engaged with the fixed scroll plate 400, and the orbiting scroll plate 300 further comprises a mounting wall 330 connected to the side of the base plate 310 facing the main bearing 700, and part of the orbiting bearing 600 is mounted in the interior of the mounting wall 330, and the outer ring of the orbiting bearing 600 is engaged with the inner wall of the mounting wall 330. In this case, the main bearing 700, the shaft balance block 10, the eccentric sleeve 500, and the orbiting bearing 600 are arranged in sequence along the axial direction of the main shaft and away from the motor 200 compared with the main bearing 700, and part of the shaft balance block 10 is arranged around the outer periphery of the mounting wall 330. Specifically, the second balance portion 12 can be arranged around the outer periphery of the eccentric sleeve 500, the orbiting bearing 600, and the mounting wall 330, so that the center of mass of the shaft balance block 10 is further close to the orbiting scroll plate 300. A shaft balance block 10 with a smaller mass can meet the shaft dynamic balance requirement of the scroll compressor, and the overall weight of the scroll compressor is reduced.

[0060] In addition, the base plate 310 is provided with an anti-rotation hole 311, and an anti-rotation ring is mounted in the anti-rotation hole 311 to prevent the orbiting scroll plate 300 from rotating while revolving relative to the fixed scroll plate 400. The base plate 310 can also be provided with a weight-reducing hole 312 arranged around the outer periphery of the mounting wall 330. The weight-reducing hole 312 can reduce the mass of the orbiting scroll plate 300, thereby reducing the eccentric mass of the shaft system of the scroll compressor. By changing the position and size of the weight-reducing hole 312, the position of the center of mass of the orbiting scroll plate 300 can be adjusted, so that the position of the center of mass of the orbiting scroll plate 300 coincides with the geometric center position, thereby avoiding the influence of the centrifugal force generated by the deviation of the center of mass of the orbiting scroll plate 300 when rotating at a high speed on the shaft dynamic balance of the scroll compressor.

[0061] The interior of the mounting wall 330 and part of the interior of the base plate 310 jointly define a mounting hole 340 for mounting the orbiting bearing 600, so that the entire outer ring of the orbiting bearing 600 is constrained by the hole wall of the mounting hole 340, and the connection between the orbiting bearing 600 and the orbiting scroll plate 300 is more stable. The mounting wall 330 has a first mounting portion 331 and a second mounting portion 332 connected along the axial direction of the orbiting scroll plate 300. The thickness of the first mounting portion 331 along the radial direction of the orbiting scroll plate 300 is greater than the thickness of the second mounting portion 332 along the radial direction of the orbiting scroll plate 300. By arranging the first mounting portion 331 and the second mounting portion 332 with different thicknesses, on the one hand, the structural strength of the mounting wall 330 is ensured to be sufficient, and the connection stability of the orbiting scroll plate 300 and the orbiting bearing 600 is improved, and on the other hand, the weight of the orbiting scroll plate 300 is reduced, thereby reducing the eccentric mass of the shaft system of the scroll compressor, which is conducive to reducing the mass of the shaft balance block 10 and / or the counterweight block 20, and thereby reducing the overall weight of the scroll compressor.

[0062] Understandably, the shaft balance block 10 is designed to conform to the outer peripheral surface of the mounting wall 330 and avoid the first mounting part 331 and the second mounting part 332. In one embodiment, the second mounting part 332 is connected to the side of the first mounting part 331 facing the main bearing 700. The connection position of the first mounting part 331 and the second mounting part 332 forms a first stepped surface. The side of the second balance part 12 facing the moving scroll 300 has a second stepped surface. There is a gap between the first stepped surface and the second stepped surface, and the first stepped surface and the second stepped surface have the same shape. This allows the shaft balance block 10 to avoid the first mounting part 331 and the second mounting part 332, and the shaft balance block 10 can be maximized to approach the moving scroll 300, thereby reducing the overall weight of the scroll compressor.

[0063] The eccentric portion 120 is configured to be integrally connected to the main body portion 110, or detachably connected to the main body portion 110. For example, the crankshaft 100 is integrally formed by machining or casting, so that the main body portion 110 and the eccentric portion 120 are formed as a single structure; or, as... Figure 2 As shown, the eccentric part 120 is configured as an eccentric pin. Part of the eccentric pin is inserted into the end of the main body 110 and fixed to the main body 110, thereby realizing a detachable connection between the eccentric part 120 and the main body 110. The fixing direction of the eccentric part 120 to the main body 110 is not limited. Part of the eccentric part 120 is inserted into the interior of the main body 110 and is interference-fitted with the main body 110. Alternatively, a threaded fastener is inserted into the main body 110 and the eccentric part 120 along the radial direction of the main body 110. The threaded fastener locks the eccentric part 120 inside the main body 110.

[0064] It should be noted that when the eccentric part 120 is configured as an eccentric pin and the eccentric pin is installed on the main body 110, the eccentric pin and the main body 110 are independent of each other. The eccentric pin is pre-processed and then installed on the end of the main body 110, which helps to reduce the radius of the eccentric pin and facilitates the processing of the main body 110. Since the eccentric sleeve 500 is sleeved on the outside of the eccentric pin, the radius of the eccentric sleeve 500 can also be adaptively reduced. The mass of the eccentric sleeve 500 and the eccentric part 120 is reduced, and the moving disc bearing 600 can be sleeved on the outside of the eccentric sleeve 500, thereby reducing the eccentric mass of the scroll compressor shaft system. This further reduces the mass of the shaft balance block 10 and the counterweight block 20, as well as the overall weight of the scroll compressor.

[0065] The first balancing part 11 of the shaft balancing block 10 is sleeved outside the main body part 110 and located between the main bearing 700 and the eccentric sleeve 500. The radius of the eccentric part 120 is smaller than the radius of the main body part 110. After the eccentric sleeve 500 is sleeved outside the eccentric part 120, the side of the eccentric sleeve 500 towards the main bearing 700 abuts against the end face of the main body part 110 towards the orbiting scroll 300. The eccentric sleeve 500 is limited by the end face of the main body part 110 and has a gap between the eccentric sleeve 500 and the shaft balancing block 10 in the axial direction of the crankshaft 100, so as to prevent the shaft balancing block 10 from vibrating and angularly deviating with the eccentric sleeve 500.

[0066] In an embodiment, referring to Figure 7 , the eccentric sleeve 500 comprises a first connecting part 510 and a second connecting part 520. The second connecting part 520 is located at one end of the first connecting part 510 and connected to the circumferential side of the first connecting part 510. The first connecting part 510 is internally provided with a through hole 511 for the eccentric part 120 to pass through. The center of the through hole 511 is eccentrically arranged compared with the center of the eccentric sleeve 500. The orbiting bearing 600 is sleeved outside the first connecting part 510. The opposite sides of the second connecting part 520 in the axial direction of the crankshaft 100 abut against the end part of the main body part 110 and the inner ring of the orbiting bearing 600 respectively, that is, the second connecting part 520 is clamped between the end part of the main body part 110 and the inner ring of the orbiting bearing 600 and remains stable in position in the axial direction of the crankshaft 100, so that a gap is always present between the eccentric sleeve 500 and the shaft balancing block 10, preventing the eccentric sleeve 500 from transmitting vibration to the shaft balancing block 10. Moreover, the orbiting bearing 600 is limited by the eccentric sleeve 500 and can abut against the side of the bottom plate 310 towards the main bearing 700, so that the orbiting scroll 300 remains stably connected with the orbiting bearing 600 and can revolve relative to the fixed scroll 400.

[0067] It should be noted that the second balancing part 12 of the shaft balancing block 10 is circumferentially arranged outside the mounting wall 330 and spaced apart from the circumferential side of the mounting wall 330 and the circumferential side of the eccentric sleeve 500 in the radial direction of the crankshaft 100, so that a gap is always present between the shaft balancing block 10 and the eccentric sleeve 500 in the axial and radial directions of the crankshaft 100, effectively preventing the eccentric sleeve 500 from transmitting vibration to the shaft balancing block 10.

[0068] The counterweight 20 can be provided in plurality. The plurality of counterweights 20 are all connected to the end face in the axial direction of the rotor 210 and all located on the side of the main bearing 700 away from the orbiting scroll 300. The plurality of counterweights 20 can all cooperate with the shaft balancing block 10 to maintain the shafting dynamic balance of the scroll compressor. The position and weight of the counterweight 20 are more flexible.

[0069] In an embodiment, at least one counterweight 20 is connected to the end of the motor 200 away from the orbiting scroll 300, so that the counterweight 20 is as far away from the main bearing 700 as possible, the rotating arm of the counterweight 20 is increased, and the mass of the counterweight 20 is reduced, which helps to reduce the overall weight of the scroll compressor.

[0070] As shown in the embodiment, one counterweight 20 is provided, and the counterweight 20 is located at the end of the motor 200 away from the orbiting scroll 300, that is, the shaft balance block 10 and the counterweight 20 cooperate to realize the dynamic balance of the shaft system of the scroll compressor, and the overall weight of the scroll compressor is maximally reduced. Figure 2

[0071] It should be noted that, in the utility model, the eccentric sleeve 500 and the shaft balance block 10 are independent and have a spacing, which can prevent the eccentric sleeve 500 from transmitting vibration to the shaft balance block 10, maintain the dynamic balance of the shaft system of the scroll compressor, and the shaft balance block 10 can be maximally close to the orbiting scroll 300 and away from the main bearing 700, so that the moment of rotational inertia opposite to the orbiting bearing 600 is also increased, the mass of the shaft balance block 10 and the counterweight 20 required for balancing the moment of rotational inertia is reduced, and the counterweight 20 is connected to the end of the rotor 210 away from the main bearing 700, so that the mass of the counterweight 20 is also reduced, thereby, the shaft balance block 10 and the counterweight 20 realize the dynamic balance of the shaft system of the scroll compressor, and the overall weight of the scroll compressor is effectively reduced.

[0072] In addition, the bearing seat 800 has a first mounting cavity 810 and a second mounting cavity 820 which are communicated in the axial direction, the main bearing 700 is located in the first mounting cavity 810, the shaft balance block 10 is located in the second mounting cavity 820, the bearing seat 800 is located between the orbiting scroll 300 and the motor 200, and the side of the bearing seat 800 facing the orbiting scroll 300 is provided with a protruding anti-rotation pin 830 which is inserted into an anti-rotation hole 311 in the bottom plate 310 to prevent the orbiting scroll 300 from rotating.

[0073] The utility model also provides a vehicle, the vehicle includes the scroll compressor, the scroll compressor can be applied to the air conditioning system in the vehicle, and the vehicle adjusts the refrigeration or heating capacity of the air conditioning system by controlling the rotating speed of the crankshaft 100 in the scroll compressor.

[0074] The vehicle in the utility model can be a private car, such as a sedan, an SUV, an MPV or a pickup truck. The vehicle can also be a commercial vehicle, such as a minivan, a bus, a small truck or a large trailer. The vehicle can be a gasoline car or a new energy car. When the vehicle is a new energy car, it can be a hybrid car or a pure electric car.

[0075] ​The utility model embodiment has been explained in detail above in combination with the drawings, but the utility model is not limited to the above-mentioned embodiment, still can make various changes in the knowledge range of the ordinary skill in the art who possesses under the premise of not departing from the utility model's tenet. Besides, the embodiment and the feature in the embodiment of the utility model can be combined mutually under the condition of not conflicting.

Claims

1. A scroll compressor, characterized by, The scroll compressor comprises: a crankshaft, comprising a main body and an eccentric part connected to one end of the main body, the eccentric part is eccentrically arranged compared to the axis of the main body; a motor connected to the main body and used to drive the rotation of the crankshaft; an eccentric sleeve sleeved on the outside of the eccentric part and in clearance fit with the eccentric part; a moving scroll in transmission connection with the eccentric sleeve through a moving disc bearing and following the rotation of the eccentric part; a main bearing sleeved on the outside of the main body along the axial direction of the crankshaft, the main bearing is located between the motor and the moving scroll; a shaft balance block fixed to the main body, the shaft balance block is located on the side of the main bearing facing the moving scroll, the shaft balance block and the eccentric sleeve are independent of each other, and the shaft balance block and the eccentric sleeve have a clearance therebetween; a counterweight connected to the end of the motor in the axial direction.

2. The scroll compressor of claim 1, wherein At least part of the shaft balance block is located between the main bearing and the moving disc bearing; and / or, the shaft balance block comprises a first balance part and a second balance part connected to the periphery of the first balance part, at least part of the second balance part is protrudingly arranged compared to the first balance part and away from the main bearing.

3. The scroll compressor of claim 1, wherein The shaft balance block and the eccentric sleeve are arranged adjacent along the axial direction of the crankshaft, and part of the shaft balance block surrounds the outer periphery of the eccentric sleeve.

4. The scroll compressor of claim 1, wherein The moving scroll comprises a bottom plate and a mounting wall connected to the side of the bottom plate facing the main bearing, part of the moving disc bearing is installed inside the mounting wall, and part of the shaft balance block surrounds the outer periphery of the mounting wall.

5. The scroll compressor of claim 4, wherein, The mounting wall has a first mounting part and a second mounting part connected along the axial direction of the moving scroll, the thickness of the first mounting part along the radial direction of the moving scroll is greater than the thickness of the second mounting part along the radial direction of the moving scroll.

6. The scroll compressor according to any one of claims 1 to 5, wherein The shaft balance block is sleeved on the outside of the main body and in interference fit with the main body.

7. The scroll compressor of claim 1, wherein The eccentric sleeve comprises a first connecting part and a second connecting part, the second connecting part is located at one end of the first connecting part and connected to the periphery of the first connecting part, the moving disc bearing is sleeved on the outside of the first connecting part, and the second connecting part abuts against the end of the main body and the inner ring of the moving disc bearing on the opposite sides in the axial direction, respectively.

8. The scroll compressor of claim 1, wherein, The eccentric part is inserted and fixed to one end of the main body.

9. The scroll compressor of claim 1, wherein, The counterweight is provided with a plurality of counterweights, at least one of the counterweights is connected to the end of the motor away from the moving scroll; or, the counterweight is provided with one counterweight and connected to the end of the motor away from the moving scroll.

10. Vehicle, characterized in that The scroll compressor comprises any one of claims 1 to 9.

Images