Pump body structure of scroll compressor, scroll compressor and air conditioner

Abstract

The application provides a pump body structure of a scroll compressor, the scroll compressor and an air conditioner. The pump body structure of the scroll compressor comprises a crankshaft and a moving disc. Part of the structure of the moving disc is sleeved with the outer periphery of the end of the crankshaft. A first helical tooth is arranged on the outer periphery wall of the end of the crankshaft. A second helical tooth is arranged on the inner periphery wall of the part of the structure of the moving disc. The first helical tooth is in helical cooperation with the second helical groove. A gap is formed between the tooth wall of the first helical tooth and the groove wall of the second helical groove matched with the first helical tooth. The lubricating oil can enter the gap. The first helical tooth can generate different forces on the oil in the gap according to different rotating speeds of the crankshaft, and then the forces act on the groove wall of the second helical groove. According to the application, different supporting forces on the moving disc can be provided according to different rotating speeds, the effect that the back pressure of the moving disc can be automatically adjusted according to different rotating speeds is realized, and the problem that the fixed back pressure cannot consider the leakage of cold quantity and the wear of the moving and static discs is solved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to a pump body structure of a scroll compressor, a scroll compressor and an air conditioner. BACKGROUND

[0002] The scroll compressor is a volumetric compression compressor, and the compression component is composed of a moving scroll plate and a fixed scroll plate. During the compression process, the relative revolution of the moving scroll plate and the fixed scroll plate forms a continuous change of the closed volume, thereby achieving the purpose of compressing the gas. Since the closed cavity formed by the engagement of the moving scroll plate and the fixed scroll plate has a certain gas pressure, the moving scroll plate will bear an axial gas force opposite to the direction of the fixed plate during compression. In order to increase the bearing life, reduce the damage of the axial force to the bearing during high-speed operation, and reduce the problems of scroll plate wear and compression chamber leakage caused by the imbalance of the axial force, it is particularly necessary to adopt a structure design that can balance the axial gas force of the moving plate. Therefore, most of the existing scroll compressor designs adopt a back pressure chamber structure. By setting mounting frames, shaft seals and other components on the back of the moving scroll plate, a closed cavity is formed on the back of the moving plate, and the intermediate pressure refrigerant between the suction pressure and the discharge pressure is introduced into the closed cavity. Due to the existence of gas pressure, an axial thrust towards the fixed plate is generated on the moving plate, thereby balancing the axial gas force generated by the compression cavity.

[0003] The conventional scroll compressor (such as the existing patent CN202111602930.0) introduces pressure gas from the moving and fixed plate compression cavity into the bottom back pressure cavity of the moving plate. The back pressure cavity is adjacent to the lubricating oil channel of the moving and fixed plate. After the scroll compressor is high-speeded, the lubricating oil film of the moving and fixed plate becomes thin, and the gas in the back pressure cavity will occupy the space of the lubricating oil, resulting in insufficient lubrication of the moving and fixed plate, and the moving and fixed plate will produce eccentric wear, which is particularly serious during ultra-high speed operation.

[0004] Since the scroll compressor in the prior art has the back pressure cavity adjacent to the lubricating oil channel of the moving and fixed plate, the pressure in the back pressure cavity will destroy the oil film, resulting in eccentric wear of the moving and fixed plate during the operation of the scroll compressor. With the increase of the rotating speed, the fixed back pressure cannot balance the leakage of cold energy and the wear of the moving and fixed plate. In some working conditions with small discharge pressure, the back pressure is insufficient at high speed, and the leakage of cold energy caused by the increase of the rotating speed of the moving and fixed plate is increased. Therefore, the present application researches and designs a pump body structure of a scroll compressor, a scroll compressor and an air conditioner. SUMMARY

[0005] Therefore, the technical problem to be solved by the present application is to overcome the defects in the prior art that the fixed back pressure cannot balance the leakage of cold energy and the wear of the moving and fixed plate with the increase of the rotating speed, thereby providing a pump body structure of a scroll compressor, a scroll compressor and an air conditioner.

[0006] To solve the above problems, the application provides a pump body structure of a scroll compressor, which comprises:

[0007] The crankshaft and the orbiting scroll, the orbiting scroll is partially structured to be sleeved on the outer periphery of the end of the crankshaft, the first helical teeth are formed on the outer periphery wall of the end of the crankshaft, the first helical grooves are formed between the adjacent two teeth of the first helical teeth along the axial direction of the crankshaft, the second helical teeth are formed on the inner periphery wall of the partially structured orbiting scroll, the second helical grooves are formed between the adjacent two teeth of the second helical teeth along the axial direction of the orbiting scroll, the first helical teeth are helically matched with the second helical grooves, the second helical teeth are helically matched with the first helical grooves, the gap is formed between the tooth wall of the first helical teeth and the groove wall of the second helical groove matched with the first helical teeth, the lubricating oil can enter the gap, the first helical teeth can generate different forces on the oil in the gap according to the different rotating speeds of the crankshaft, and then the forces are applied to the groove wall of the second helical groove to provide the support force for the orbiting scroll.

[0008] In some embodiments, the higher the rotating speed of the crankshaft is, the greater the force of the first helical teeth on the oil in the gap is, and then the greater the support force on the orbiting scroll is; the lower the rotating speed of the crankshaft is, the smaller the force of the first helical teeth on the oil in the gap is, and then the smaller the support force on the orbiting scroll is.

[0009] In some embodiments, the first helical teeth comprise the first upper tooth wall above the axial direction of the crankshaft and the first lower tooth wall below the axial direction, the second helical grooves comprise the first upper groove wall above the axial direction of the crankshaft and the first lower groove wall below the axial direction, the gap comprises the first gap between the first upper tooth wall and the first upper groove wall and the second gap between the first lower tooth wall and the first lower groove wall, the first upper tooth wall is in contact with the first upper groove wall when the scroll compressor is not started, at least part of the gravity of the orbiting scroll is transmitted to the first upper tooth wall through the first upper groove wall, and then transmitted to the crankshaft through the first helical teeth; the lubricating oil enters the first gap between the first upper tooth wall and the first upper groove wall after the scroll compressor is started, so that the crankshaft provides the support force for the orbiting scroll through the first helical teeth and the lubricating oil in turn.

[0010] In some embodiments, the first lower tooth wall is not in contact with the first lower groove wall when the scroll compressor is not started, and the second gap is greater than 0; the first lower tooth wall is in contact with the first lower groove wall after the scroll compressor is started, so that the second gap is 0.

[0011] The volume of the first gap gradually increases and the volume of the second gap gradually decreases during the process from the non-starting to the starting of the scroll compressor.

[0012] In some embodiments, the first spiral tooth comprises a first tooth end at a radially outermost end, the second spiral groove comprises a second groove end at a radially outermost end, in the mutually matched first tooth end and second groove end, there is a gap three between the first tooth end and the second groove end in a radial direction, the gap three comprises the gap three, the gap three is communicated between the gap one and the gap two, and the gap three is always greater than 0 during the process of the scroll compressor from non-starting to starting.

[0013] In some embodiments, a groove is further formed on the first lower tooth wall of the first spiral tooth to form a spiral tooth bottom surface oil channel, the first lower groove wall is attached to the first lower tooth wall after the scroll compressor is started, the spiral tooth bottom surface oil channel can be communicated with the gap three to release the oil pressure in the gap one through the spiral tooth bottom surface oil channel.

[0014] In some embodiments, the spiral tooth bottom surface oil channel is a plurality of spiral tooth bottom surface oil channels, and the plurality of spiral tooth bottom surface oil channels are sequentially and spacedly arranged along the spiral direction of the first spiral tooth, and the plurality of spiral tooth bottom surface oil channels are relatively arranged along the axial direction of the crankshaft.

[0015] In some embodiments, the crankshaft comprises a driving end portion at one axial end thereof, the orbiting scroll comprises an orbiting scroll sleeve protruding towards the crankshaft, the orbiting scroll sleeve is a cylindrical structure, the driving end portion is a columnar structure, the orbiting scroll sleeve is sleeved on the driving end portion, the first spiral tooth is formed on the outer peripheral wall of the driving end portion and spirally extends along the axial direction of the crankshaft, and the second spiral tooth is formed on the inner peripheral wall of the orbiting scroll sleeve and spirally extends along the axial direction of the orbiting scroll sleeve.

[0016] In some embodiments, the inside of the crankshaft is provided with a central oil hole in the axial direction, a containing cavity is formed between the axial end of the driving end portion and the orbiting scroll, one end of the containing cavity is communicated with the central oil hole, and the other end is communicated with the gap, so that the lubricating oil enters the gap through the containing cavity.

[0017] In some embodiments, a bracket is further provided, the bracket supports the crankshaft, a back pressure cavity is further formed between the bracket and the orbiting scroll, one axial end of the gap is communicated with the containing cavity along the axial direction of the crankshaft, and the other axial end is communicated with the back pressure cavity, so that the lubricating oil enters the back pressure cavity through the gap, and the lubricating oil in the back pressure cavity provides back pressure to the orbiting scroll; and the orbiting scroll is not provided with a back pressure communication channel communicated between the compression cavity and the back pressure cavity.

[0018] In some embodiments, a static disk is further included, which cooperates with the dynamic disk to form the compression cavity therebetween, at least one dynamic-static disk lubricating oil groove is formed at the joint of the static disk and the dynamic disk, one end of the dynamic-static disk lubricating oil groove is communicated with the back pressure cavity to be able to suck in lubricating oil, a first oil discharge channel is arranged on the static disk, a second oil discharge channel is arranged on the support, the pump body structure further includes an oil amount adjusting bolt, the oil amount adjusting bolt is arranged from the first oil discharge channel to the second oil discharge channel, one end of the first oil discharge channel is communicated with the dynamic-static disk lubricating oil groove, one end of the second oil discharge channel is communicated with the other end of the first oil discharge channel, and the other end of the second oil discharge channel is communicated with the space below the support.

[0019] The application further provides a scroll compressor comprising the pump body structure of any one of the preceding scroll compressors.

[0020] The application further provides an air conditioner comprising the scroll compressor.

[0021] The pump body structure of a scroll compressor, the scroll compressor and the air conditioner provided by the application have the following advantages

[0022] Advantages:

[0023] 1. The first helical teeth are arranged on the outer peripheral wall of the end portion of the crankshaft, the first helical teeth are adjacent to each other in the axial direction, and a first helical groove is formed between the two adjacent teeth, thereby forming an external thread structure on the crankshaft; the second helical teeth are arranged on the inner peripheral wall of the dynamic disk, the second helical teeth are adjacent to each other in the axial direction, and a second helical groove is formed between the two adjacent teeth, thereby forming an internal thread structure on the dynamic disk; when the dynamic disk is installed, the dynamic disk is screwed onto the end portion of the crankshaft through the internal and external thread structures, a gap is formed between the first helical teeth and the second helical groove, and the lubricating oil in the crankshaft can enter the gap; the first helical teeth can act on the oil in the gap through a certain force during the rotation of the crankshaft, the force is transmitted to the groove wall of the second helical groove of the dynamic disk through the oil, the rotation speed of the crankshaft changes in size, the first helical teeth can act on the oil through different forces at different rotation speeds, thereby providing different support forces on the dynamic disk according to different rotation speeds, effectively realizing the effect that the back pressure of the dynamic disk can be automatically adjusted according to different rotation speeds, solving the problem that the fixed back pressure cannot balance the leakage of cold energy and the wear of the dynamic and static disks, providing different back pressures according to different rotation speeds, solving the problem of insufficient back pressure at high rotation speed under some working conditions with small exhaust pressure, solving the problem that the leakage of refrigeration capacity increases due to the increase of rotation speed of the dynamic and static disks, improving the reliability of high speed and optimizing the performance of the compressor.

[0024] 2. The present application can also make the back pressure cavity entirely occupied by lubricating oil, without introducing medium pressure gas therein, so as to provide back pressure to the orbiting scroll solely by the oil in the back pressure cavity, and the oil pressure in the back pressure cavity and the support force generated by the rotation of the first spiral tooth jointly act on the orbiting scroll, so as to improve the sealing performance between the fixed scroll and the orbiting scroll under working condition, prevent refrigeration capacity leakage, eliminate the oil film failure between the fixed scroll and the orbiting scroll caused by the introduction of the medium pressure in the compression cavity into the back pressure cavity, and make the fixed back pressure pressure play the effect of preventing refrigeration capacity leakage and preventing the wear of the fixed scroll and the orbiting scroll. BRIEF DESCRIPTION OF DRAWINGS

[0025] Figure 1 is a partial longitudinal sectional view of a scroll compressor of the prior art;

[0026] Figure 2 is a partial longitudinal sectional view of a scroll compressor of the present application;

[0027] Figure 3 is Figure 2 is a partial enlarged view of part I in

[0028] Figure 4a is Figure 3 is a partial enlarged view of part II in a stationary state of

[0029] Figure 4b is a partial enlarged view of part II in a moving state of Figure 3

[0030] Figure 5 is a partial view of a crankshaft part of the scroll compressor of the present application.

[0031] Reference signs are indicated as:

[0032] 1, fixed scroll; 10, compression cavity; 11, fixed-orbiting scroll lubricating oil groove; 12, first oil discharge passage; 2, orbiting scroll; 21, second spiral tooth; 22, second spiral groove; 221, first upper groove wall; 222, first lower groove wall; 223, second groove end; 23, orbiting scroll shaft sleeve; 3, crankshaft; 31, first spiral tooth; 311, first upper tooth wall; 312, first lower tooth wall; 313, first tooth end; 314, spiral tooth bottom oil channel; 32, first spiral groove; 33, driving end part; 34, center oil hole; 35, accommodating cavity; 4, bracket; 41, second oil discharge passage; 5, oil amount adjusting bolt; 6, gap; 61, gap one; 62, gap two; 63, gap three; 7, back pressure cavity. DETAILED DESCRIPTION

[0033] As​Figures 2-5 The application provides a pump body structure of a scroll compressor, which comprises:

[0034] The crankshaft 3 and the movable disc 2, the outer peripheral wall of the end portion of the crankshaft 3 is sleeved with the partial structure of the movable disc 2, the first helical tooth 31 is arranged on the outer peripheral wall of the end portion of the crankshaft 3, the first helical groove 32 is formed between the adjacent two teeth of the first helical tooth 31 along the axial direction of the crankshaft 3, the second helical tooth 21 is arranged on the inner peripheral wall of the partial structure of the movable disc 2, the second helical groove 22 is formed between the adjacent two teeth of the second helical tooth 21 along the axial direction of the movable disc 2, the first helical tooth 31 is matched with the second helical groove 22, the second helical tooth 21 is matched with the first helical groove 32, the gap 6 is formed between the tooth wall of the first helical tooth 31 and the groove wall of the second helical groove 22 matched with the tooth wall, the lubricating oil can enter the gap 6, the first helical tooth 31 can generate different forces on the oil in the gap 6 due to different rotating speeds of the crankshaft 3, and then the forces are applied to the groove wall of the second helical groove 22, so that the support force is provided for the movable disc 2.

[0035] The application forms the outer thread structure on the crankshaft by arranging the first helical tooth on the outer peripheral wall of the end portion of the crankshaft sleeved with the movable disc and forming the first helical groove between the adjacent two teeth of the first helical tooth along the axial direction, and the inner thread structure on the inner peripheral wall of the movable disc by arranging the second helical tooth on the inner peripheral wall of the movable disc and forming the second helical groove between the adjacent two teeth of the second helical tooth along the axial direction, so that the movable disc is screwed to the end portion of the crankshaft by the inner and outer thread structure when the movable disc is installed, the gap is formed between the first helical tooth and the second helical groove, the lubricating oil in the crankshaft can enter the gap, the first helical tooth can generate a certain force on the oil in the gap due to the rotation of the crankshaft, the force is transmitted to the groove wall of the second helical groove of the movable disc through the oil, the different forces are generated on the oil due to the change of the rotating speed of the crankshaft, the different support forces are provided for the movable disc according to the different rotating speeds, the different support forces are provided for the movable disc according to the different rotating speeds, the effect that the back pressure of the movable disc can be automatically adjusted according to the different rotating speeds is realized, the problem that the fixed back pressure cannot consider the leakage of cold energy and the wear of the movable and static discs is solved, the different back pressures are provided according to the different rotating speeds, the problems of the leakage of refrigerant and the wear of the movable and static discs are solved, the effect that the back pressure of the movable disc can be automatically adjusted according to the different rotating speeds is realized, the problem that the back pressure is insufficient under the high rotating speed in some working conditions with small exhaust pressure is solved, the problem that the refrigeration capacity is increased due to the increase of the rotating speed of the movable and static discs is solved, the high-speed reliability is improved, and the performance of the compressor is optimized.

[0036] The present application adopts a spiral structure designed at the upper end of the crankshaft of the scroll compressor and the matching part of the moving disc, an upward oil pressure thrust is generated by the rotation of the crankshaft, and acts on the bottom of the moving disc, so as to realize the adjustment of the back pressure of the moving disc with the rotating speed, eliminate the oil film failure caused by the back pressure of the moving and static disc, and reduce the cold leakage caused by the insufficient back pressure at high rotating speed under some working conditions with small exhaust pressure.

[0037] The following technical problems are solved:

[0038] The scroll compressor is adjacent to the lubricating oil path of the moving and static disc in the back pressure cavity, and the pressure in the back pressure cavity can destroy the oil film, so that the moving and static disc generates eccentric wear during the operation of the scroll compressor. With the increase of the rotating speed, the fixed back pressure cannot balance the cold leakage and the wear of the moving and static disc. Under some working conditions with small exhaust pressure, the insufficient back pressure at high rotating speed causes the cold leakage of the moving and static disc due to the increase of the rotating speed.

[0039] In some embodiments, the higher the rotating speed of the crankshaft 3 is, the greater the force of the first spiral tooth 31 acting on the oil in the gap 6 is, and the greater the supporting force of the moving disc 2 is; the lower the rotating speed of the crankshaft 3 is, the smaller the force of the first spiral tooth 31 acting on the oil in the gap 6 is, and the smaller the supporting force of the moving disc 2 is.

[0040] This is a further preferred structure of the present application, that is, the supporting force of the first spiral tooth acting on the moving disc is increased with the increase of the rotating speed of the crankshaft. Since the greater the rotating speed of the crankshaft is, the faster the rotating speed of the moving scroll is, and the higher the pressure in the compression chamber is, the greater the probability of the leakage of the moving scroll from the static scroll is. Therefore, at this time, the supporting force of the first spiral tooth acting on the moving disc is increased, so as to automatically increase the back pressure of the moving disc, thereby effectively preventing the leakage between the moving and static discs, improving the sealing performance, and ensuring the normal and effective operation of the compressor. Similarly, if the rotating speed of the crankshaft is reduced, the supporting force of the first spiral tooth acting on the moving disc is reduced. The smaller the rotating speed of the crankshaft is, the smaller the pressure in the compression chamber is, and the smaller the probability of the leakage of the moving disc from the static disc is. At this time, the back pressure should be reduced, otherwise the wear degree between the moving and static discs will be increased. However, the present application automatically reduces the supporting force of the moving disc by the structure of the first spiral tooth (the centrifugal force of the first spiral tooth is generated by rotation, and the component force of the centrifugal force acts on the inclined surface of the groove wall of the moving disc through the tooth inclined surface, so as to generate the supporting force of the moving disc), so as to automatically and effectively reduce the wear between the moving and static discs, and ensure the sealing performance.

[0041] In some embodiments, the first helical tooth 31 comprises a first upper tooth wall 311 located above in the axial direction of the crankshaft 3 and a first lower tooth wall 312 located below in the axial direction, the second helical groove 22 comprises a first upper groove wall 221 located above in the axial direction of the crankshaft 3 and a first lower groove wall 222 located below in the axial direction, the gap 6 comprises a first gap 61 between the first upper tooth wall 311 and the first upper groove wall 221 and a second gap 62 between the first lower tooth wall 312 and the first lower groove wall 222, the first upper tooth wall 311 and the first upper groove wall 221 are in contact when the scroll compressor is not started, at least part of the gravity of the orbiting scroll 2 is transmitted to the first upper tooth wall 311 through the first upper groove wall 221, and then transmitted to the crankshaft 3 through the first helical tooth 31; after the scroll compressor is started, lubricating oil enters the first gap 61 between the first upper tooth wall 311 and the first upper groove wall 221, so that the crankshaft 3 provides support force to the orbiting scroll 2 through the first helical tooth 31 and lubricating oil in turn.

[0042] This is a further preferred structure of the first helical tooth and the second helical groove of the present application, that is, the first helical tooth comprises a first upper tooth wall and a first lower tooth wall, and the second helical groove comprises a first upper groove wall and a first lower groove wall, at least part of the gravity of the orbiting scroll is supported on the first upper tooth wall through the first upper groove wall when the compressor is static (stopped), and the two form a fit, which can generate a certain degree of gravity support to the orbiting scroll through the crankshaft, and after the compressor is started, lubricating oil will flow into the gap one between the first upper tooth wall and the first upper groove wall to separate the gap one, the centrifugal force generated by the rotation of the first upper tooth wall acts on the oil in the gap one, and then acts on the orbiting scroll, thereby automatically providing support force to the orbiting scroll according to the size of the rotating speed during the starting process, effectively preventing leakage between the orbiting scroll and the fixed scroll due to too small back pressure, and automatically preventing wear between the orbiting scroll and the fixed scroll due to too large back pressure.

[0043] In some embodiments, the first lower tooth wall 312 and the first lower groove wall 222 are not in contact when the scroll compressor is not started, forming a gap two 62 greater than 0; after the scroll compressor is started, the first lower tooth wall 312 and the first lower groove wall 222 are in contact, so that the gap two 62 is 0.

[0044] During the process from not starting to starting of the scroll compressor, the volume of the first gap 61 gradually increases, and the volume of the second gap 62 gradually decreases.

[0045] This is the preferred structure between the first helical tooth and the second helical groove of the present application, that is, the first upper groove wall of the orbiting scroll is in contact with the first upper tooth wall to form a gravity support when the compressor is not started, at this time, the gap two is formed between the first lower groove wall and the first lower tooth wall, which is used to accommodate the lubricating oil to enter, thereby providing the lubricating oil for the gap two at the lower end, so as to discharge the oil to the lower side of the orbiting scroll into the back pressure cavity; after the compressor is started, the orbiting scroll is supported upward and moves upward due to the gap one between the first upper tooth wall and the first upper groove wall, to the first lower groove wall and the first lower tooth wall in contact, at this time, the first helical tooth provides an upward supporting force to the orbiting scroll, so that the gap two is reduced to 0; during the process from not starting to starting, the volume of the gap one gradually increases from 0 to the maximum, and the volume of the gap two gradually decreases from the maximum to 0, so that the orbiting scroll is supported by the first upper tooth wall in contact with the first upper tooth wall of the first helical tooth from not starting, and gradually moves upward to be supported by the centrifugal force provided by the first upper tooth wall and the oil, so that the orbiting scroll is closely in contact with the stationary scroll, preventing the refrigerant from leaking, improving the sealing performance, and improving the operating performance of the compressor.

[0046] Figure 3 The arrow direction is the direction of the movement of the lubricating oil, and the continuous oil pumping promotes the movement of the oil in the arrow direction to fill the entire cavity. The spiral oil groove can increase the centrifugal force acting on the oil as the speed increases, and then act on the orbiting scroll.

[0047] Figures 4a-4b The arrow direction is the direction of the movement of the oil, and the continuous oil pumping promotes the movement of the oil in the arrow direction to fill the entire cavity. The spiral oil groove can increase the centrifugal force acting on the oil as the speed increases, and then act on the orbiting scroll.

[0048] In some embodiments, the first helical tooth 31 comprises a first tooth end 313 at the radially outermost end, and the second helical groove 22 comprises a second groove end 223 at the radially outermost end, wherein the first tooth end 313 and the second groove end 223 are matched with each other, and a gap three 63 is formed between the first tooth end 313 and the second groove end 223 in the radial direction. The gap 6 comprises the gap three 63, and the gap three 63 is communicated between the gap one 61 and the gap two 62. The gap three 63 is always greater than 0 during the process of the scroll compressor from non-starting to starting. This is a further preferred structure of the first helical tooth and the second helical groove of the present application. By keeping the gap three at the radially outer end of the first tooth end and the second groove end, oil can pass from the gap one to the gap two through the gap three (from starting to stopping, so that the oil is discharged downward into the back pressure chamber), and also pass from the gap two to the gap one through the gap three (from stopping to starting), so that the oil can enter the gap one upward to support the orbiting scroll.

[0049] As Figures 4a-4b , Figure 5 In some embodiments, the first lower tooth wall 312 of the first helical tooth 31 is further provided with a groove to form a helical tooth bottom oil channel 314. When the scroll compressor is started, the first lower groove wall 222 is in contact with the first lower tooth wall 312, and the helical tooth bottom oil channel 314 can be communicated with the gap three 63 to release the oil pressure in the gap one 61. The present application can effectively release the pressure in the gap one after the compressor is started, that is, by controlling the size and number of the gap three 63, the pressure of the oil accumulated in the gap one 61 can be adjusted. The oil pressure accumulated in the gap one 61 produces a circumferential pressure, and the upward component force acts on the top of the first lower groove wall 221 to lift the orbiting scroll. The volume of the oil in the gap one 61 increases with the increase of the rotating speed, and the resulting pressure also increases. This prevents the situation that the oil cannot be discharged downward into the back pressure chamber after stopping because the first lower tooth wall cannot enter the lubricating oil in the gap two. The helical tooth bottom oil channel can regulate the oil pressure in the gap one to ensure that the orbiting scroll produces an upward axial force.

[0050] In some embodiments, the helical tooth bottom oil channel 314 is one or more, and a plurality of helical tooth bottom oil channels 314 are sequentially and spacedly arranged along the helical direction of the first helical tooth 31, and a plurality of helical tooth bottom oil channels 314 are relatively arranged along the axial direction of the crankshaft 3. This is a further preferred structure of the helical tooth bottom oil channel of the present application, which can release the pressure in the gap one in each axial direction to ensure that the lubricating oil can enter the gap two.

[0051] Figure 5 The spiral crankshaft oil channel diagram is shown in the figure, the central oil hole of the crankshaft is the main oil channel for pumping oil upward, and the oil channel is arranged at the bottom of the spiral tooth of the crankshaft and used for axial pressure relief to ensure that the dynamic disc generates upward axial force. The oil channel at the bottom of the spiral tooth of the crankshaft is not limited to the position and number shown in the figure, and a plurality of oil channels can be arranged on the dynamic disc. Figure 5

[0052] In some embodiments, the crankshaft 3 comprises a driving end 33 at one axial end thereof, the dynamic disc 2 comprises a dynamic disc sleeve 23 arranged protruding towards the crankshaft 3, the dynamic disc sleeve 23 is a cylindrical structure, the driving end 33 is a columnar structure, the dynamic disc sleeve 23 is sleeved on the driving end 33, the first spiral tooth 31 is arranged on the outer peripheral wall of the driving end 33 and spirally extends along the axial direction of the crankshaft 3, and the second spiral tooth 21 is arranged on the inner peripheral wall of the dynamic disc sleeve 23 and spirally extends along the axial direction of the dynamic disc sleeve 23. This is a further preferred structure of the crankshaft and the dynamic disc of the present application, that is, the part of the structure of the crankshaft cooperating with the dynamic disc is the driving end, the part of the structure of the dynamic disc cooperating with the crankshaft is the dynamic disc sleeve, the cylindrical dynamic disc sleeve is sleeved on the driving end, the first spiral tooth is a spiral tooth arranged on the outer peripheral wall of the driving end, and the second spiral tooth is also a spiral tooth structure arranged on the dynamic disc sleeve, so that the thread connection between the dynamic disc and the crankshaft is formed.

[0053] In some embodiments, the inside of the crankshaft 3 is provided with a central oil hole 34 in the axial direction, and a containing cavity 35 is formed between the axial end of the driving end 33 and the dynamic disc 2, one end of the containing cavity 35 communicates with the central oil hole 34, and the other end communicates with the gap 6, so that the lubricating oil enters the gap 6 through the containing cavity 35. The present application also introduces oil from the central oil hole into the containing cavity through the structure of the central oil hole in the inside of the crankshaft and the containing cavity at the end thereof, and the oil in the containing cavity can enter the gap between the first spiral tooth and the second spiral groove, thereby providing effective oil pressure support for the support of the dynamic disc during the rotation of the crankshaft, and effectively solving the problems of cold leakage and dynamic and static disc wear.

[0054] ​In some embodiments, a support 4 is further included, which forms a support for the crankshaft 3, and a back pressure cavity 7 is further formed between the support 4 and the orbiting scroll 2, and the gap 6 along the axial direction of the crankshaft 3 is communicated with the containing cavity 35 at one axial end and communicated with the back pressure cavity 7 at the other axial end, so that the lubricating oil can enter the back pressure cavity 7 through the gap 6, and the back pressure force can be provided to the orbiting scroll 2 by the lubricating oil in the back pressure cavity 7; and the orbiting scroll 2 is not provided with a back pressure communication channel which communicates the compression cavity 10 and the back pressure cavity 7. The back pressure cavity structure can be formed between the support and the orbiting scroll, and the back pressure cavity is only communicated with the gap between the first helical tooth and the second helical groove, and the orbiting scroll is not provided with a back pressure communication channel, so that the back pressure cavity is entirely occupied by the lubricating oil, and the medium pressure gas is not introduced into the back pressure cavity, so that the back pressure force is provided to the orbiting scroll by the oil in the back pressure cavity only, the oil pressure in the back pressure cavity and the support force generated by the rotation of the first helical tooth jointly act on the orbiting scroll, the sealing performance of the orbiting scroll and the fixed scroll under the working state is improved, the refrigeration capacity leakage is prevented, and the oil film failure between the orbiting scroll and the fixed scroll caused by the introduction of the medium pressure in the compression cavity into the back pressure cavity is eliminated, the fixed back pressure force can prevent the refrigeration capacity leakage and the orbiting scroll and the fixed scroll wear as the rotation speed is improved.

[0055] Figure 2 The structure assembly drawing of the present application is mainly composed of an upper support, an orbiting scroll, a fixed scroll and a crankshaft. When the compressor crankshaft rotates, the lubricating oil is pressed into the upper end of the crankshaft by the oil pump at the bottom of the crankshaft; the oil hole at the upper end of the crankshaft enters the helical oil groove through the bottom of the orbiting scroll, the lubricating oil moves downward through the helical oil groove, and then enters the back pressure cavity at the bottom of the orbiting scroll; after the back pressure cavity is filled, the lubricating oil enters the lubricating oil channel of the orbiting scroll and the fixed scroll, and continuously lubricates the contact surface of the orbiting scroll and the fixed scroll; the pressure of the back pressure cavity can be adjusted by the oil amount adjusting bolt, and the excess lubricating oil can flow back to the bottom of the crankshaft through the oil amount adjusting bolt, forming a complete circulation. The structure cancels the back pressure cavity on the orbiting scroll and the fixed scroll, fills the back pressure cavity with lubricating oil, eliminates the oil film failure caused by the back pressure of the orbiting scroll and the fixed scroll, and improves the high speed reliability.

[0056] In some embodiments, a static disc 1 is further included, which cooperates with the dynamic disc 2 to form the compression cavity 10 therebetween, at least one dynamic-static disc lubricating oil groove 11 is formed at the joint of the static disc 1 and the dynamic disc 2, one end of the dynamic-static disc lubricating oil groove 11 communicates with the back pressure cavity 7 to be able to suck in lubricating oil, a first oil discharge channel 12 is arranged on the static disc 1, a second oil discharge channel 41 is arranged on the support 4, the pump body structure further includes an oil amount adjusting bolt 5, the oil amount adjusting bolt 5 is arranged from the first oil discharge channel 12 into the second oil discharge channel 41, one end of the first oil discharge channel 12 communicates with the dynamic-static disc lubricating oil groove 11, one end of the second oil discharge channel 41 can communicate with the other end of the first oil discharge channel 12, and the other end of the second oil discharge channel 41 communicates with the space below the support 4.

[0057] The first oil discharge channel arranged on the static disc and the second oil discharge channel arranged on the support can effectively discharge the excess oil in the dynamic-static disc lubricating oil groove, and the oil amount adjusting bolt can adjust the amount of discharged oil to meet the demand for the oil amount in the actual working process.

[0058] The application further provides a scroll compressor comprising the pump body structure of the scroll compressor.

[0059] The application adopts the spiral structure designed at the joint of the upper end of the crankshaft of the scroll compressor and the dynamic disc, and the upward oil pressure thrust generated by the rotation of the crankshaft acts on the bottom of the dynamic disc to realize the adjustment of the back pressure of the dynamic disc with the rotation speed, solve the oil film failure caused by the back pressure of the dynamic-static disc, reduce the problems such as the increased cold leakage of the dynamic-static disc caused by the insufficient back pressure at high rotation speed under some working conditions with small exhaust pressure, and improve the high-speed reliability and optimize the performance.

[0060] The application further provides an air conditioner comprising the scroll compressor.

[0061] The above only describes the preferred embodiments of the application and should not be used to limit the application, and any modification, equivalent replacement and improvement made within the spirit and principle of the application should be included in the protection scope of the application. The above only describes the preferred embodiments of the application, and it should be pointed out that, for ordinary skilled in the art, without departing from the technical principles of the application, a number of improvements and modifications can be made, and these improvements and modifications should be regarded as the protection scope of the application.

Claims

1. A pump body structure of a scroll compressor, characterized by: The application relates to a pump body structure of a scroll compressor, which comprises a crankshaft (3) and a moving disc (2), the moving disc (2) is sleeved with part of a structure on the outer periphery of the end of the crankshaft (3), a first helical tooth (31) is arranged on the outer periphery wall of the end of the crankshaft (3), a first helical groove (32) is formed between two adjacent teeth of the first helical tooth (31) along the axial direction of the crankshaft (3), a second helical tooth (21) is arranged on the inner periphery wall of part of the structure of the moving disc (2), a second helical groove (22) is formed between two adjacent teeth of the second helical tooth (21) along the axial direction of the moving disc (2), the first helical tooth (31) is in helical cooperation with the second helical groove (22), the second helical tooth (21) is in helical cooperation with the first helical groove (32), a gap (6) is formed between the tooth wall of the first helical tooth (31) and the groove wall of the second helical groove (22) matched with the tooth wall, lubricating oil can enter the gap (6), the first helical tooth (31) can generate different acting forces on the oil in the gap (6) due to different rotating speeds of the crankshaft (3), and then the acting forces are applied to the groove wall of the second helical groove (22) to provide a supporting force for the moving disc (2). The first helical tooth (31) comprises a first upper tooth wall (311) located above along the axial direction of the crankshaft (3) and a first lower tooth wall (312) located below along the axial direction, the second helical groove (22) comprises a first upper groove wall (221) located above along the axial direction of the crankshaft (3) and a first lower groove wall (222) located below along the axial direction, the gap (6) comprises a first gap (61) between the first upper tooth wall (311) and the first upper groove wall (221) and a second gap (62) between the first lower tooth wall (312) and the first lower groove wall (222), the first upper tooth wall (311) is in contact with the first upper groove wall (221) when the scroll compressor is not started, at least part of the gravity of the moving disc (2) is transmitted to the first upper tooth wall (311) through the first upper groove wall (221), and then the first upper tooth wall (311) is transmitted to the crankshaft (3) through the first helical tooth (31); after the scroll compressor is started, lubricating oil enters the first gap (61) between the first upper tooth wall (311) and the first upper groove wall (221), so that the crankshaft (3) provides a supporting force for the moving disc (2) through the first helical tooth (31) and the lubricating oil in sequence.

2. The pump body structure of the scroll compressor according to claim 1, wherein the higher the rotating speed of the crankshaft (3) is, the greater the acting force of the first helical tooth (31) on the oil in the gap (6) is, and then the greater the supporting force of the moving disc (2) is; the lower the rotating speed of the crankshaft (3) is, the smaller the acting force of the first helical tooth (31) on the oil in the gap (6) is, and then the smaller the supporting force of the moving disc (2) is.

3. The pump body structure of the scroll compressor according to claim 1, wherein ​ ​ The first lower tooth wall (312) is not connected with the first lower groove wall (222) when the scroll compressor is not started, forming the gap two (62) greater than 0; after the scroll compressor is started, the first lower tooth wall (312) is connected with the first lower groove wall (222), so that the gap two (62) is 0. During the process from not starting to starting of the scroll compressor, the volume of the gap one (61) gradually increases, and the volume of the gap two (62) gradually decreases.

4. The pump body structure of the scroll compressor according to claim 3, characterized in that: The first spiral tooth (31) comprises a first tooth end (313) located at the radially outermost end, and the second spiral groove (22) comprises a second groove end (223) located at the radially outermost end, wherein the first tooth end (313) and the second groove end (223) have a gap three (63) between them in the radial direction in the matching first tooth end (313) and the second groove end (223), the gap (6) comprises the gap three (63), the gap three (63) is connected between the gap one (61) and the gap two (62), and the gap three (63) is always greater than 0 during the process from not starting to starting of the scroll compressor.

5. The pump body structure of the scroll compressor according to claim 4, characterized in that: The first lower tooth wall (312) of the first spiral tooth (31) is further provided with a groove, forming a spiral tooth bottom surface oil channel (314), and when the first lower groove wall (222) is attached to the first lower tooth wall (312) after the scroll compressor is started, the spiral tooth bottom surface oil channel (314) can be connected with the gap three (63) to release the oil pressure in the gap one (61) through the spiral tooth bottom surface oil channel (314).

6. The pump body structure of the scroll compressor according to claim 5, characterized in that: The spiral tooth bottom surface oil channel (314) is a plurality of, and the plurality of spiral tooth bottom surface oil channels (314) are sequentially and spaced apart along the spiral direction of the first spiral tooth (31), and the plurality of spiral tooth bottom surface oil channels (314) are relatively arranged along the axial direction of the crankshaft (3).

7. The pump body structure of the scroll compressor according to any one of claims 1-6, characterized in that: The crankshaft (3) comprises a driving end portion (33) located at one end in the axial direction, the orbiting scroll (2) comprises an orbiting scroll sleeve (23) protruding towards the crankshaft (3), the orbiting scroll sleeve (23) is a cylindrical structure, the driving end portion (33) is a columnar structure, the orbiting scroll sleeve (23) is sleeved on the driving end portion (33), the first spiral tooth (31) is formed on the outer peripheral wall of the driving end portion (33) and spirally extends along the axial direction of the crankshaft (3), and the second spiral tooth (21) is formed on the inner peripheral wall of the orbiting scroll sleeve (23) and spirally extends along the axial direction of the orbiting scroll sleeve (23).

8. The pump body structure of the scroll compressor according to claim 7, characterized in that: The crankshaft (3) is provided with a central oil hole (34) in the axial direction, and a containing cavity (35) is formed between the shaft end of the driving end (33) and the orbiting scroll (2), one end of the containing cavity (35) is communicated with the central oil hole (34), and the other end is communicated with the gap (6), so that the lubricating oil enters the gap (6) through the containing cavity (35).

9. The pump body structure of the scroll compressor according to claim 8, characterized in that: The bracket (4) is further provided between the bracket (4) and the orbiting scroll (2), and the gap (6) is communicated with the containing cavity (35) in the axial direction of the crankshaft (3), and the other end is communicated with the back pressure cavity (7), so that the lubricating oil can enter the back pressure cavity (7) through the gap (6), and the back pressure cavity (7) can provide back pressure to the orbiting scroll (2); and the orbiting scroll (2) is not provided with a back pressure communication channel communicated with the compression cavity (10) and the back pressure cavity (7).

10. The pump body structure of the scroll compressor according to claim 9, characterized in that: The stationary scroll (1) is further provided between the stationary scroll (1) and the orbiting scroll (2) to form the compression cavity (10) therebetween, and at least one orbiting and stationary scroll lubricating oil groove (11) is formed at the joint of the stationary scroll (1) and the orbiting scroll (2), one end of the orbiting and stationary scroll lubricating oil groove (11) is communicated with the back pressure cavity (7) to suck in lubricating oil; the stationary scroll (1) is provided with a first oil discharge channel (12), the bracket (4) is provided with a second oil discharge channel (41), and the pump body structure further comprises an oil amount adjusting bolt (5), the oil amount adjusting bolt (5) is arranged from the first oil discharge channel (12) to the second oil discharge channel (41), one end of the first oil discharge channel (12) is communicated with the orbiting and stationary scroll lubricating oil groove (11), one end of the second oil discharge channel (41) is communicated with the other end of the first oil discharge channel (12), and the other end of the second oil discharge channel (41) is communicated with the space below the bracket (4).

11. A scroll compressor characterized by: The pump body structure of the scroll compressor according to any one of claims 1-10.

12. An air conditioner characterized by comprising: The scroll compressor according to claim 11.

Images