Roller vane assembly and compressor

Abstract

The present invention relates to the technical field of compressor manufacturing, and discloses a roller vane assembly and a compressor. The roller vane assembly comprises a roller and a vane movably connected to one side of the roller, one of the vane and the roller is provided with a hooking structure, and the other is provided with a hooking matching structure, and the hooking structure and the hooking matching structure are engaged with each other in a point contact manner to achieve a hooking connection between the vane and the roller. The roller and the vane of the present invention are connected by hooking, and the running follow-up reliability is higher, and the phenomenon of separation of the roller and the vane can be effectively avoided, low-frequency noise vibration is improved, low-frequency performance is guaranteed, and leakage and low-frequency rattling sound caused by separation of the two are prevented.

Description

Technical Field

[0001] The invention relates to the technical field of compressor manufacturing, and in particular to a roller sliding vane assembly and a compressor. Background Art

[0002] The rolling rotor compressor is mainly composed of two parts: the pump body and the motor. Figure 1 to Figure 2 As shown, the pump assembly mainly includes a cylinder 40a, a crankshaft 30a, a roller A10a, a vane A20a, an upper flange 50a, and a lower flange 60a. The crankshaft 30a of the pump body is interference-fitted with the motor rotor. The R surface of the vane A20a head abuts against the outer circle of the roller A10a under the action of the pump body back pressure and the spring force, thereby dividing the internal volume composed of the cylinder 40a and the roller A10a into two crescent-shaped suction chambers 70a and compression chambers 80a. Its working principle is that the crankshaft 30a rotates periodically under the driving force of the motor, and drives the roller A10a to rotate synchronously and eccentrically through its eccentric structure, thereby driving the vane A20a to do radial reciprocating motion in the vane groove of the cylinder 40a, so that the volume of the suction chamber 70a and the compression chamber 80a changes accordingly, thereby realizing the process of periodic suction, compression, and exhaust of the compressor.

[0003] At present, there are great limitations to improving the efficiency and reducing the noise of compressors based solely on structural optimization design. For the moving parts of the pump body, if their weight cannot be reduced, the wear, vibration and noise problems caused by the movement process are extremely obvious. Especially during the low-frequency operation of the compressor, or during the process of increasing the frequency from low frequency to a higher speed, the risk of the vanes and rollers coming off is high, which will cause rattling noises and wear and leakage problems, which will have a great impact on the performance of the whole machine. Summary of the invention

[0004] In view of this, the present invention provides a roller vane assembly and a compressor to solve the problems of wear, vibration and noise in the compressor during movement in the prior art.

[0005] In a first aspect, the present invention provides a roller slide assembly, comprising:

[0006] Roller;

[0007] A sliding plate, movably connected to one side of the roller;

[0008] One of the sliding plate and the roller is provided with a hooking structure, and the other is provided with a hooking matching structure. The hooking structure and the hooking matching structure are engaged with each other in a point contact manner to achieve a hooking connection between the sliding plate and the roller.

[0009] Beneficial effect: By means of a hooking structure provided on one of the vane and the roller and a hooking matching structure provided on the other, a hook connection between the roller and the vane is achieved. Compared with the conventional way in which the R surface of the vane head abuts against the outer circle of the roller under the action of the pump body back pressure and the spring force, the operation tracking reliability is higher, and the separation of the roller and the vane can be effectively avoided, and low-frequency noise and vibration can be improved. It can effectively ensure the following reliability of the roller and the vane under various working conditions, ensure low-frequency performance, and prevent the separation of the two to cause leakage and low-frequency rattling noise.

[0010] In addition, in the present invention, the roller and the sliding vane are connected by an innovative hooking method. This structural connection has high reliability and can ensure that the sliding vane and the roller are connected under any conditions. During operation, the roller can still swing and retain part of the rotation. Moreover, the hooking structure and the hooking matching structure are point contact. Compared with the existing hinged connection method between the sliding vane and the roller, the contact area is smaller and the friction power consumption is significantly lower. Therefore, in the present invention, the roller and the sliding vane are connected by hooking, which has obvious advantages in improving energy efficiency and improving noise, and can effectively solve the problems of wear, vibration and noise of the compressor in the prior art during movement.

[0011] In an optional embodiment, the hooking structure includes a hook head provided at one end of the sliding sheet close to the roller, and the hooking matching structure includes a hooking groove provided on the outer peripheral surface of the roller.

[0012] Beneficial effects: By setting a hook groove on the outer surface of the roller and a hook head at the end of the sliding vane, the two cooperate with each other to be connected by hooking. During operation, the roller can still swing and retain part of the rotation. Compared with the conventional connection structure, the roller and the sliding vane provided by the present invention do not have the phenomenon of separation under various working conditions and frequency points, and the followability is greatly guaranteed. The leakage of high and low pressure refrigerant caused by the separation of the roller and the sliding vane is eliminated, and the energy efficiency of the compressor operation is guaranteed. It can effectively solve the problem of the clicking sound caused by the separation of the roller and the sliding vane at low frequency. At the same time, the spring can also be cancelled, and the tail end of the sliding vane groove adopts a closed design. The hook head and the hook groove are in two-point line contact. Compared with the hinged connection method, the contact area is small and the friction power consumption is significantly lower. In addition, the hook structure and the hook matching structure adopt the form of a hook head and a hook groove, which is simple in structure and convenient for processing and forming.

[0013] In an optional embodiment, the hook head is a C-shaped hook head, one end of the C-shaped hook head is a base and the other end is a hook connection portion;

[0014] An anti-slipping portion is arranged on one side of the hooking groove corresponding to the hooking portion, and the anti-slipping portion and the hooking portion are engaged with each other.

[0015] Beneficial effects: The hook head adopts the structure of a C-type hook head, which is reliable and has a good anti-hooking effect. In addition, by providing an anti-hooking part on one side of the hooking part of the C-type hook head corresponding to the hooking groove, the anti-hooking part can engage with the hooking parts, thereby effectively preventing the hook head from being detached from the hooking groove, thereby improving the reliability of the roller and the slider's running follow-up, effectively ensuring the low-frequency performance, and avoiding the problem of rattling noise caused by the detachment of the slider and the roller.

[0016] In an optional embodiment, the minimum wall thickness of the anti-slip portion is d1, d1≥3 mm; and / or the minimum wall thickness of the C-shaped hook head is d2, d2≥3 mm.

[0017] Beneficial effect: Since the compressor has a long service life requirement, and the roller and the vane are the main moving parts of the compressor pump body, their reliability requirements are relatively high. Therefore, the minimum thicknesses d1 and d2 of the hooking parts of the roller and the vane are set to d1≥3mm and d2≥3mm respectively, thereby effectively ensuring the fatigue strength of the hooking parts of the roller and the vane during operation and improving the reliability of the operation of the whole machine.

[0018] In an optional embodiment, the minimum wall thickness between the hook groove and the inner circumference of the roller is set to D, and D≥2.5 mm.

[0019] Beneficial effect: By setting the minimum wall thickness of the inner wall of the hooking groove to be no less than 2.5 mm from the inner circle of the roller, the structural strength of the roller can be effectively guaranteed, making it less likely for the roller to deform during processing and operation.

[0020] In an optional embodiment, the edges of the hook head and the hook groove are rounded or streamlined.

[0021] Beneficial effect: By setting the hook groove of the roller and the edges of the hook head of the sliding plate to rounded corners or other streamlined transition designs, it is possible to prevent the refrigerant gas from generating eddy currents at the edges of the hooking part of the roller and the sliding plate when flowing through the roller.

[0022] In an optional embodiment, the rollers and / or the sliding vanes are arranged in layers along the axial direction of the rollers, and the rollers and / or the sliding vanes are made of ceramic material.

[0023] Beneficial effects: By designing the rollers and / or vanes in a layered combination along the axial direction, the end face leakage can be effectively reduced, and by making the rollers and / or vanes of ceramic materials, due to the physical properties of ceramic materials with low density, high hardness and good wear resistance, the weight of parts can be greatly reduced, and the low-frequency noise and vibration problems of the compressor can be improved. The problem that conventional pump body parts are made of metal materials such as cast iron and alloy steel, which have a relatively high density due to the inherent characteristics of the materials, so the mass of each component is relatively large and the wear resistance is poor, resulting in a large relative stress between the two parts after the components move relative to each other under load conditions, which is prone to abnormal wear problems, and the vibration and noise levels are also poor.

[0024] In an optional embodiment, the sliding plate includes at least two sub-slide plates stacked in the axial direction of the roller, and the at least two sub-slide plates are made of at least two ceramic materials.

[0025] Beneficial effect: Since the weight of the existing ceramic material with lower density is greatly reduced, its linear expansion coefficient is much lower than that of conventional high-speed steel, resulting in the gradual increase of the end face clearance of the vane as the temperature of the pump body increases during high-frequency operation. It may be difficult to form an oil film, and there is a risk of refrigerant leaking from the low-pressure side to the high-pressure side through the end face of the vane, which is not conducive to the energy efficiency of the compressor. Therefore, in this embodiment, the sub-vanes are processed with at least two or more ceramic materials with different linear expansion coefficients, such as AlSiC, zirconia, etc., which can greatly reduce the weight of parts and improve the low-frequency noise and vibration of the compressor. At the same time, each sub-vane can be processed according to the specific axial clearance requirements. Different ceramic materials are selected and used in combination to adjust the overall axial clearance, improve sealing, and meet the pump body clearance requirements.

[0026] In an optional embodiment, the rollers and the sliding plates are arranged in layers; the layered surfaces of the rollers and the layered surfaces of the sliding plates are arranged alternately.

[0027] Beneficial effect: After the rollers and vanes are layered, the staggered arrangement of the roller and vane layers can effectively avoid the overlap of the sub-roller and sub-vane layers, which can prevent the parts from moving radially, thereby affecting the stability of the oil film, causing leakage, and increasing friction power consumption.

[0028] In an optional embodiment, the sliding sheets are layered in unequal ratios.

[0029] Beneficial effect: Due to the difference in linear expansion coefficients of different ceramic materials, the change in shaft height is different. According to the actual axial matching clearance requirements, if the slider is layered in equal proportions, it means that multiple materials need to be used in combination to meet the clearance requirements. By setting the slider in unequal layers, the axial assembly clearance value can be adjusted synchronously by adjusting the height of the layered sub-slide while adjusting the clearance using ceramic materials with different linear expansion coefficients, thereby reducing the number of layers and parts, and facilitating the clearance adjustment of the axial end face of the slider.

[0030] In a second aspect, the present invention further provides a compressor comprising the roller vane assembly of any one of the above embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] In order to more clearly illustrate the specific implementation methods of the present invention or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0032] Figure 1 It is a structural schematic diagram of a pump body assembly (without the upper and lower flanges) in the prior art;

[0033] Figure 2 It is a cross-sectional view of a pump body assembly in the prior art;

[0034] Figure 3 It is a schematic diagram of a structure in which a roller and a sliding plate are connected by a hinge in the prior art;

[0035] Figure 4 It is a schematic structural diagram of a roller slide assembly (slides are layered in equal proportions) in an embodiment of the present invention;

[0036] Figure 5 for Figure 4 Side view of

[0037] Figure 6 A side view of a roller slide assembly (slides with unequal ratio layers) in an embodiment of the present invention;

[0038] Figure 7 A top view of the roller slide assembly in the embodiment of the present invention when the slide is fully retracted;

[0039] Figure 8 for Figure 7 Schematic diagram of the structure of the middle slide;

[0040] Fig. 9 for Figure 7 Schematic diagram of the structure of the middle roller;

[0041] Fig.10 A top view of the roller slide assembly in the embodiment of the present invention at the suction deflection limit position;

[0042] Fig.11 A top view of the roller vane assembly in the embodiment of the present invention at the exhaust deflection limit position;

[0043] Fig.12 It is a partial enlarged view of the hooking part of the roller slide assembly in the embodiment of the present invention.

[0044] Description of the reference numerals of the background art:

[0045] 10a, roller A; 20a, vane A; 30a, crankshaft; 40a, cylinder; 50a, upper flange; 60a, lower flange; 70a, suction chamber; 80a, compression chamber;

[0046] Description of the accompanying drawings in this application:

[0047] 10. roller; 101. sub-roller; 11. hooking groove; 111. anti-slip part;

[0048] 20. Slide; 201. Sub-slide; 21. Hook head; 211. Base; 212. Hooking part. DETAILED DESCRIPTION

[0049] In order to make the purpose, technical solution and advantages of the embodiments of the present invention clearer, the technical solution in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative work are within the scope of protection of the present invention.

[0050] Combined with the current development status of the industry, there are great limitations to simply optimizing the design to improve the efficiency and reduce the noise of the compressor. How to make further breakthroughs on the existing research level of rotary compressors has become a bottleneck problem. At present, the pump body parts of compressors are mostly made of metals such as cast iron. Due to the limitations of their material properties, they are relatively heavy. Especially for the moving parts of the pump body, when their weight cannot be reduced, the wear, vibration and noise problems caused by the movement process are extremely obvious. In addition, during the low-frequency operation of the compressor, the rattling sound and leakage caused by the separation and wear of the vanes and rollers also have a great impact on its noise and performance.

[0051] Some related patents provide a roller vane structure with an integrated design of the vane and the roller. The integrated roller vane is layered along the axial direction to increase the number of gap surfaces to reduce the leakage of refrigerant oil from high pressure to low pressure from each gap surface, and prevent the high-temperature refrigerant oil flowing out from the high-pressure side from heating the gas on the low-pressure side and affecting the overall energy efficiency level. However, under this structure, since the adjacent roller vanes are designed as an integrated unit, the radial end surface area between the two adjacent parts in the axial direction increases, the leakage channel becomes larger, and there is a significant adverse effect on the energy efficiency of the compressor. At the same time, the rollers of this structure cannot rotate on their own, so the friction power consumption between the inner circle of the roller and the outer circle of the eccentric part of the crankshaft increases significantly.

[0052] Some related patents provide roller vane structures, in which rollers and vanes are designed with axial layering, which can reduce the overall leakage by increasing the number of gap surfaces and improve the energy efficiency of the compressor; in addition, Figure 3 As shown, in this structure, a hinge joint is provided at the head of the sliding vane A20a, and a hinge groove is provided at the outer side of the roller A10a. The two are connected in correspondence, which can restrain the layered rollers, radial misalignment of the sliding vane and other asynchronous movements, and at the same time ensure the movement followability of the sliding vane and the roller. However, under this hinged structure, the hinged head of the sliding vane A20a is nested in the corresponding hinge groove of the roller A10a. Although this solution can also solve the roller sliding vane followability problem, with the current development trend of small displacement and high speed of compressors, if the operating frequency is increased to a certain limit, such as if the compressor is upgraded to a higher speed, the roller drives the sliding vane to reciprocate. When the hinge binding force between the two is less than the reverse inertia force of the parts, the sliding vane still has the risk of detaching from the hinge groove of the roller, and the two may still detach. In addition, the hinged head and the hinge groove of the roller are in surface contact, which increases the friction power consumption.

[0053] Therefore, the embodiments of the present invention are intended to at least solve the following technical problems existing in conventional rolling rotor compressors:

[0054] 1. Compressor pump parts are limited by conventional metal materials, and have problems such as heavy weight, low-frequency noise, large vibration, and easy wear of parts.

[0055] 2. During the low-frequency operation of the compressor, or during the process of increasing the frequency from low frequency to a higher speed, there is a high risk of the vanes and rollers detaching, which will cause rattling noise and wear and leakage problems, which will have a significant impact on the performance of the entire machine.

[0056] Combine the following Figures 4 to 12 , describing an embodiment of the present invention.

[0057] According to an embodiment of the present invention, on the one hand, the present invention provides a roller slide assembly, comprising: a roller 10 and a slide 20, the slide 20 being movably connected to one side of the roller 10; one of the slide 20 and the roller 10 is provided with a hook structure, and the other is provided with a hook matching structure, the hook structure and the hook matching structure are engaged with each other in a point contact manner to realize the hook connection between the slide 20 and the roller 10.

[0058] In the above embodiment, by means of a hooking structure provided on one of the vane 20 and the roller 10 and a hooking matching structure provided on the other, the roller 10 and the vane 20 are hooked and connected. Compared with the conventional vane head R surface abutting against the outer circle of the roller 10 under the action of the pump body back pressure and the spring force, the operation tracking reliability is higher, and the separation of the roller 10 and the vane 20 can be effectively avoided, and the low-frequency noise vibration can be improved. It can effectively ensure the roller-vane tracking reliability under various working conditions, ensure the low-frequency performance, and prevent the separation of the two to cause leakage and low-frequency rattling sound.

[0059] In addition, in the present invention, the roller 10 and the vane 20 are connected by an innovative hooking method. This structural connection has high reliability and can ensure that the vane 20 is connected to the roller 10 under any conditions. During operation, the roller 10 can still swing and retain part of its rotation. Moreover, the hooking structure and the hooking matching structure are point contact. Compared with the existing hinged connection method between the vane 20 and the roller 10, the contact area is smaller and the friction power consumption is significantly lower. Therefore, in the present invention, the roller 10 and the vane 20 are connected by hooking, which has obvious advantages in improving energy efficiency and improving noise, and can effectively solve the problems of wear, vibration and noise of the compressor in the prior art during movement.

[0060] In some embodiments, the hooking structure includes a hook head 21 disposed on one end of the sliding sheet 20 close to the roller 10 , and the hooking matching structure includes a hooking groove 11 disposed on the outer peripheral surface of the roller 10 .

[0061] In the above embodiment, by setting the hook groove 11 on the outer circumference of the roller 10, the end of the slide 20 is provided with a hook head 21, and the two cooperate with each other to connect in a hooking manner. During operation, the roller 10 can still swing and retain part of the rotation. Compared with the conventional connection structure, the roller 10 and the slide 20 provided by the present invention do not have the phenomenon of separation in various working conditions and frequency points, and the followability is greatly guaranteed. The leakage of high and low pressure refrigerant caused by the separation of the roller and the slide is eliminated, and the energy efficiency of the compressor operation is guaranteed. It can effectively solve the problem of the clacking sound caused by the separation of the roller and the slide at low frequency. At the same time, the spring can also be cancelled, and the tail end of the slide groove adopts a closed design. The hook head 21 and the hook groove 11 are in two-point line contact. Compared with the hinged connection method, the contact area is small and the friction power consumption is significantly lower. In addition, the hook structure and the hook matching structure adopt the form of the hook head 21 and the hook groove 11, which is simple in structure and convenient for processing.

[0062] Specifically, in this embodiment, the hook head 21 is disposed at one end of the sliding sheet 20 close to the roller 10 , and the hooking groove 11 is a groove structure provided on the outer peripheral surface of the roller 10 , and the hook head 21 can be hooked in the hooking groove 11 .

[0063] Of course, in other alternative embodiments, the hooking structure and the hooking mating structure may also adopt a two-hook structure. Preferably, in order to reduce the size of the outer circumference of the roller 10 and avoid the protruding hook from affecting the rotation of the roller 10, the hooking mating structure on the roller 10 adopts a hooking groove structure.

[0064] In some embodiments, in combination Figures 4 to 9 As shown, the hook head 21 is a C-shaped hook head, one end of the C-shaped hook head is a base 211 and the other end is a hooking portion 212; an anti-slip portion 111 is provided on one side of the hooking groove 11 corresponding to the hooking portion 212, and the anti-slip portion 111 and the hooking portion 212 are engaged with each other.

[0065] In the above embodiment, the hook head 21 adopts a C-type hook head structure, which is reliable and has a good anti-unhooking effect. In addition, the anti-unhooking portion 111 is arranged on one side of the hook portion 212 of the C-type hook head corresponding to the hook groove 11. The anti-unhooking portion 111 can engage with the hook portion 212, thereby effectively preventing the hook head 21 from being separated from the hook groove 11, thereby improving the reliability of the running follow-up of the roller 10 and the slide 20, effectively ensuring the low-frequency performance, and avoiding the problem of rattling noise caused by the separation of the slide 20 and the roller 10.

[0066] Specifically, Figures 7 to 9As shown, the base 211 at one end of the C-shaped hook is fixedly connected to the main body of the slide 20 or is integrally formed, and the other end is a hook portion 212 suitable for hooking with the roller 10. Preferably, the C-shaped hook is integrally formed with the slide 20. An anti-slip portion 111 is provided on one side of the hook portion 212 in the hook groove 11. The end of the anti-slip portion 111 is bent and extended to the opposite side to tighten the notch of the hook groove 11, and the anti-slip portion 111 can resist the limiting hook portion 212 at the notch, thereby effectively preventing the C-shaped hook from slipping out of the hook groove 11. Fig. 9 As shown, the entire hooking groove 11 is shaped like a tiger's mouth, and the end of the anti-slip portion 111 not only extends to the opposite side but also bends inward at a certain angle, so as to effectively hook the C-shaped hook head.

[0067] In some embodiments, an anti-slip portion 111 is provided on one side of the hooking groove 11, and a set swing gap is provided between the other side and the C-shaped hook head. There is also a certain movable space between the hooking portion 212 of the C-shaped hook head and the anti-slip portion 111, so that the roller 10 can still swing during the operation of the compressor to retain the function of partial rotation.

[0068] In some embodiments, Fig.12 As shown, the minimum wall thickness of the anti-slip portion 111 is d1, d1≥3mm; and / or the minimum wall thickness of the C-shaped hook head is d2, d2≥3mm. Preferably, both d1 and d2 are not less than 3mm.

[0069] In the above embodiment, since the compressor has a long service life requirement, and the roller 10 and the vane 20 are the main moving parts of the compressor pump body, their reliability requirements are relatively high. Therefore, the minimum thicknesses d1 and d2 of the hooking parts of the roller 10 and the vane 20 are set to d1 ≥ 3 mm and d2 ≥ 3 mm, respectively, so as to effectively ensure the fatigue strength of the hooking parts of the roller 10 and the vane 20 during operation and improve the reliability of the operation of the whole machine.

[0070] In some optional embodiments, such as Figure 7 , Figure 8 The thickness of the hooking portion 212 of the C-shaped hook head is greater than the thickness of the base 211. Such a design can increase the structural strength of the hooking portion 212. Fig.12 As shown, in the present embodiment, the minimum wall thickness of the C-shaped hook head is located at the base 211, and the thickness of the entire C-shaped hook head shows a trend of first narrowing, then increasing, and then remaining unchanged from the base 211 toward the hook portion 212. The minimum wall thickness is located at the base 211. By setting the thickness of the base 211 within a size range of not less than 3 mm, the risk of breakage due to the base 211 being too thin can be effectively avoided during operation, which can easily lead to the problem of the slide 20 and the roller 10 being detached.

[0071] Furthermore, if Figures 7 to 9 as well as Fig.12 As shown, the thickness of the end of the anti-slip portion 111 is smaller than the thickness at other positions, and the thickness of the entire anti-slip portion 111 tends to gradually narrow and then remain unchanged. Specifically, the anti-slip portion 111 includes a transition section and a curved hook section. The transition section is located between the curved hook section and the roller 10. The thickness of the curved hook section remains unchanged and is bent at a certain angle toward the inside of the hooking groove 11 to stably hook with the hooking portion 212.

[0072] In this embodiment, the thickness of the end of the anti-slip portion 111 (that is, the curved hook section) is the smallest. By setting the end wall thickness of the anti-slip portion 111 to be no less than 3 mm, the structural strength of the end of the anti-slip portion 111 can be effectively guaranteed, and the stability of the curved hook section when resisting and hooking with the hooking portion 212 can be ensured.

[0073] In some embodiments, Fig.12 As shown, the minimum wall thickness between the hook groove 11 and the inner circumference of the roller 10 is set to D, D ≥ 2.5 mm.

[0074] In the above embodiment, by setting the minimum wall thickness of the inner wall of the hooking groove 11 to be not less than 2.5 mm from the inner circle of the roller 10, the structural strength of the roller 10 can be effectively ensured, making it difficult for the roller 10 to deform during processing and operation.

[0075] In some embodiments, the edges of the hook head 21 and the hooking groove 11 are rounded or streamlined.

[0076] In the above embodiment, by setting the edges of the hooking groove 11 of the roller 10 and the hook head 21 of the sliding vane 20 to be rounded or other streamlined transition designs, it is possible to prevent the refrigerant gas from generating eddy currents at the edges of the hooking parts of the roller 10 and the sliding vane 20 when flowing through them.

[0077] Specifically, combined Figures 7 to 12 As shown, the entire hook head 21 is a smooth C-shaped structure, the inner wall of the hooking groove 11 is also arc-shaped, and the wall surfaces at the ends of the hook head 21 and the anti-slip portion 111 are both arc-shaped structures with smooth transition.

[0078] In some embodiments, the rollers 10 and / or the sliding vanes 20 are arranged in layers along the axial direction of the rollers 10 , and the rollers 10 and / or the sliding vanes 20 are made of ceramic material.

[0079] In the above embodiment, the roller 10 and / or the vane 20 are designed to be layered and combined along the axial direction to effectively reduce the end face leakage, and the roller 10 and / or the vane 20 are made of ceramic material. Since the ceramic material has the physical properties of low density, high hardness and good wear resistance, the weight of the parts can be greatly reduced, and the low-frequency noise and vibration problems of the compressor can be improved. The problem that conventional pump body parts are made of metal materials such as cast iron and alloy steel, which have a relatively high density due to the inherent characteristics of the material, so the mass of each component is relatively large and the wear resistance is poor, resulting in a large relative stress between the two parts after the components move relative to each other under load conditions, which is prone to abnormal wear problems, and the vibration and noise levels are also poor.

[0080] Specifically, in this embodiment, the slide 20 is designed in layers along the axial direction, and the roller 10 can also be layered. Preferably, the roller 10 and the slide 20 are both designed in a layered splicing style. The number of layers of the roller 10 is set to k1, and the number of layers of the slide 20 is set to k2, which must satisfy: k1 ≥ 1, k2 ≥ 2. Therefore, the gap surface of the roller 10 and the slide 20 increases the number of gap end faces compared to the conventional structure. For example, the slide 20 is optimized from a conventional single integral slide 20 to a layered design of two upper and lower sub-slides 201 spliced ​​together, and the number of gap end faces is increased from 2 to 3. The two sub-slides 201 are spliced ​​together to form three gap end faces in the vertical direction: upper, middle and lower. is the end face leakage, , is the gap between the upper and lower end faces, according to the following formula:

[0081] ① Leakage from the upper and lower ends of the slide 20 to the front chamber (i.e., the compression chamber):

[0082] ② Leakage through the upper and lower ends of the slide 20 to the rear cavity (i.e. the suction cavity): , it can be seen that the leakage amount and the gap value are in a cubic relationship.

[0083] Since the clearance between the sliding vane 20 and the upper and lower flanges is constant, the total clearance of the conventional sliding vane 20 , and the total gap of the layered splicing slide 20 , in comparison: Therefore, the leakage of the layered spliced ​​vane 20 will also be less than that of the conventional vane 20, thereby reducing the total leakage value of the compressor. Similarly, the same conclusion applies to the layered design of the roller 10. Among them, a and b refer to the gaps between the upper and lower end surfaces of the normal vane 20 and the upper and lower flanges. a', b', and c refer to the three gap values ​​formed in the vertical direction after the layered spliced ​​vane 20 is used, and c is the gap between the two sub-vanes 201.

[0084] For example: suppose the total end face clearance value of the conventional slider 20 is 6, then if a and b are distributed in equal proportions to 3 each, then a³+b³=54; and after adopting the layered slider 20, a³=b³=c=2, so the total value of the cube is 2³+2³+2³=24, and it is obvious that 54>24.

[0085] It needs to be explained that in the end face leakage theory, gas and liquid will leak from the front cavity to the rear cavity along the end face gap. In the compressor, the front cavity refers to the compression cavity of the cylinder, and the rear cavity refers to the suction cavity of the cylinder. Affected by the pressure difference, the high-pressure gas in the compression cavity will leak to the low-pressure side of the suction cavity through the leakage channel on the end face of the slide vane 20.

[0086] In some embodiments, the sliding sheet 20 includes at least two sub-slide sheets 201 stacked along the axial direction of the roller 10 , and the at least two sub-slide sheets 201 are made of at least two ceramic materials.

[0087] In the above embodiment, although the weight of the existing ceramic material with lower density is greatly reduced, its linear expansion coefficient is much lower than that of conventional high-speed steel, resulting in that as the temperature of the pump body increases during high-frequency operation, the end face clearance of the vane 20 gradually increases, and it may be difficult to form an oil film. There is a risk of refrigerant leaking from the low-pressure side to the high-pressure side through the end face of the vane 20, which is not conducive to the energy efficiency of the compressor. Therefore, in this embodiment, the sub-vane 201 is processed by at least two or more ceramic materials with different linear expansion coefficients, such as AlSiC, zirconia, etc., which can greatly reduce the weight of parts and improve the low-frequency noise and vibration of the compressor. At the same time, each sub-vane 201 can be processed according to the specific axial clearance requirements. Different ceramic materials are selected and used in combination to adjust the overall axial clearance, improve sealing, and meet the pump body clearance requirements.

[0088] In this embodiment, there are at least two sub-slides 201. When there are two sub-slides 201, the two sub-slides 201 are processed using two ceramic materials; when the number of sub-slides 201 is three or more, at least two sub-slides 201 are formed by processing different ceramic materials, such as AlSiC, zirconia, etc.

[0089] The roller 10 can be processed by metal or ceramic material at the same time. Preferably, the roller 10 is also processed by ceramic material.

[0090] For example, Figure 5 and Figure 6 As shown, the slide 20 includes three sub-slides 201 arranged in sequence from top to bottom, and the three sub-slides 201 are made of at least two ceramic materials, for example, the uppermost and middle sub-slides 201 are made of AlSiC, and the lowermost sub-slide 201 is made of zirconia. Figure 5As shown, △h1, △h2, and △h3 are the axial height changes of each sub-vane 201 under the high-frequency stable state of the compressor under the influence of temperature rise, and this change will affect the axial clearance of the vane 20. The maximum axial height change of the vane 20 when the compressor is running under the high-frequency stable state is set to △H=△h1+△h2+△h3. According to this design, each sub-vane 201 can be processed with different ceramic materials according to the specific axial clearance requirements to adjust the overall axial clearance and improve the sealing.

[0091] The roller vane assembly provided in the present embodiment is designed by axially layering the vane 20 and the roller 10, each sub-vane 201 is processed with different ceramic materials, and the vane 20 and the roller 10 are connected by hooking, which can effectively improve end face leakage, reduce the weight of the vane 20, improve low-frequency noise and vibration, and ensure the following reliability of the roller vane under various working conditions, ensure low-frequency performance, and avoid the occurrence of rattling noise.

[0092] In some embodiments, Figures 4 to 6 As shown, the roller 10 and the sliding vane 20 are arranged in layers along the axial direction of the roller 10 , and the layered surfaces of the roller 10 and the layered surfaces of the sliding vane 20 are arranged alternately in the axial direction of the roller 10 .

[0093] In the above embodiment, after the roller 10 and the vane 20 are layered, by staggering the layered surfaces of the roller 10 and the vane 20, it is possible to effectively avoid the overlap of the layered surfaces of the sub-rollers 101 and the sub-vane 201, and avoid radial movement of the parts, thereby affecting the stability of the oil film, causing leakage, and increasing friction power consumption.

[0094] In this embodiment, the head of each sub-slide 201 is designed with a hook head 21 of the same size, and the contact position between the outer circle of each sub-roller 101 and the slide 20 is designed with a hook groove 11 of the same size.

[0095] In some embodiments, Figure 6 As shown, the vane 20 is layered in unequal proportions. Due to the difference in linear expansion coefficients of different ceramic materials, the change in shaft height is different. According to the actual axial matching clearance requirements, if the vane 20 is layered in equal proportions, it means that multiple materials need to be used in combination to meet the clearance requirements. By adopting the setting of unequally layered vanes 20, it is possible to adjust the axial assembly clearance value by adjusting the height of the layered sub-slide 201 while adjusting the clearance using ceramic materials with different linear expansion coefficients, thereby reducing the number of layers and the number of parts, and facilitating the clearance adjustment of the axial end face of the vane 20.

[0096] Of course, in other alternative embodiments, such as Figure 5 As shown, the sliding vane 20 can also be normally layered in equal proportions. Preferably, in this embodiment, the sliding vane 20 is layered in unequal proportions.

[0097] The roller vane assembly provided by the present invention effectively reduces leakage by designing a layered combination of the vane 20 and the roller 10 along the axial direction, wherein the sub-vane 201 is processed by two or more ceramic materials to reduce the overall mass of the vane 20, improve the noise and vibration during the operation of the vane 20, and enhance the wear resistance of the parts. At the same time, it can also improve the risk of leakage caused by the end face gap of the vane 20 increasing with the increase of the operating frequency due to the linear expansion coefficient of the ceramic material being lower than that of cast iron. The roller 10 material can also be simultaneously processed with metal or ceramic; in addition, the roller 10 and the vane 20 in the present invention are innovatively connected by hooking, and this structural connection has high reliability, and can ensure that the vane 20 is connected to the roller 10 under any conditions, and the roller 10 can still swing and retain part of the rotation during operation.

[0098] In summary, the main improvements of the roller slide assembly provided in this embodiment are as follows:

[0099] 1. The roller 10 and the sliding vane 20 adopt a layered design to improve the end surface leakage problem;

[0100] 2. The roller 10 and the slide 20 are made of ceramic materials to reduce the weight of moving parts and improve noise and vibration;

[0101] 3. A variety of ceramic materials are combined to form the roller 10 and the vane 20. The vane 20 is layered in equal or unequal proportions, and the axial clearance can be adjusted according to the clearance requirements;

[0102] 4. The roller slide is connected by hooking to prevent the two from separating and causing leakage and low-frequency rattling noise.

[0103] According to an embodiment of the present invention, on the other hand, a compressor is provided, comprising the roller vane assembly of any one of the above-mentioned embodiments.

[0104] Preferably, the compressor is a rotary compressor.

[0105] The compressor provided by the present invention optimizes the pump body structure. The roller 10 and the vane 20 adopt an axially layered combination design, which can effectively improve the leakage problem during the operation of the compressor and improve the energy efficiency level. By replacing the roller 10 and the vane 20 with ceramic materials, the weight of the moving parts related to the pump body can be reduced, and the vibration and noise can be improved. In addition, the roller 10 and the vane 20 are innovatively connected by hooking, and the operation tracking reliability is high. There is no separation phenomenon, which effectively guarantees the low-frequency performance and avoids the occurrence of low-frequency clicking noise.

[0106] It should be noted that the roller vane assembly provided by the present invention is not only applicable to rotary compressors, but also applicable to rotary fluid machinery with similar structures, such as rotary expanders, vane compressors, vane expanders, and the like.

[0107] Although the embodiments of the present invention are described in conjunction with the accompanying drawings, those skilled in the art may make various modifications and variations without departing from the spirit and scope of the present invention, and such modifications and variations shall all fall within the protection scope of the embodiments of the present application.

Claims

1. A roller slide assembly, characterized in that: include: Roller (10); A sliding plate (20) movably connected to one side of the roller (10); One of the sliding plate (20) and the roller (10) is provided with a hooking structure, and the other is provided with a hooking matching structure, the hooking structure and the hooking matching structure are engaged with each other in a point contact manner to achieve a hooking connection between the sliding plate (20) and the roller (10); The hook structure comprises a hook head (21) arranged at one end of the sliding sheet (20) close to the roller (10), the hook matching structure comprises a hook groove (11) arranged on the outer peripheral surface of the roller (10), the hook head (21) is a C-shaped hook head, one end of the C-shaped hook head is a base (211), and the other end is a hook portion (212); The hook groove (11) is provided with an anti-slip portion (111) on one side corresponding to the hook portion (212), and the anti-slip portion (111) and the hook portion (212) are engaged with each other; the slide (20) is arranged in layers along the axial direction of the roller (10), the slide (20) comprises at least two sub-slides (201) stacked in the axial direction of the roller (10), and the at least two sub-slides (201) are made of at least two ceramic materials; the slide (20) is layered in unequal proportions.

2. The roller slide assembly according to claim 1, characterized in that: The minimum wall thickness of the anti-slip portion (111) is d1, d1≥3 mm; and / or the minimum wall thickness of the C-shaped hook head is d2, d2≥3 mm.

3. The roller slide assembly according to any one of claims 1 to 2, characterized in that: The minimum wall thickness between the hook groove (11) and the inner circumferential surface of the roller (10) is set to D, and D is ≥ 2.5 mm.

4. The roller slide assembly according to any one of claims 1 to 2, characterized in that: The edges of the hook head (21) and the hook groove (11) are rounded or streamlined.

5. The roller slide assembly according to any one of claims 1 to 2, characterized in that: The rollers (10) are arranged in layers along the axial direction of the rollers (10), and the rollers (10) are made of ceramic material.

6. The roller slide assembly according to claim 5, characterized in that: The layered surfaces of the roller (10) and the layered surfaces of the sliding sheet (20) are arranged alternately.

7. A compressor, characterized in that: A roller slide assembly comprising any one of claims 1 to 6.

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