Large-modulus and small-tooth-difference internal meshing gear rotor compressor

Abstract

The invention discloses an internal meshing gear rotor compressor with large modulus and small tooth difference. Comprising an air cylinder and a piston, the piston is arranged in an inner cavity of the air cylinder, the inner cavity of the air cylinder is provided with a gear ring with a concave arc tooth profile with the tooth number z, the piston is a planet gear with a convex arc tooth profile with the tooth number z-1, the tooth difference between the piston and the air cylinder is 1, and z is larger than or equal to 2; the piston is meshed with the air cylinder, the piston reversely revolves around the axis of the air cylinder with the eccentricity delta e as the radius while rotating, the air cylinder is divided into z independent compression cavities, when the piston rotates by a circle, the z compression cavities sequentially complete air suction, compression and exhaust for z-1 times, and the revolution speed of the piston is z-1 times of the rotation speed of the piston. The invention has the advantages of simple structure, low noise, small vibration, long service life and the like.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressors, and particularly relates to an internal meshing gear rotor compressor with large module and few teeth difference. Background Art

[0002] A compressor is a fluid machine that compresses low-pressure gas into high-pressure gas, provides power for the refrigeration cycle, and is the heart of an air-conditioning system.

[0003] Common existing gas compressors include piston compressors, rolling rotor compressors, scroll compressors, etc. For piston compressors, such as the "crankshaft for piston compressor and piston compressor having the same" disclosed in Chinese invention patent publication CN104819127A, in this solution, the piston movement forces the volume of the compression chamber to change, and there are deficiencies such as large vibration, large inertial force, large noise, and obvious gas pulsation; for example, the "turbine compressor and refrigerator" disclosed in Chinese invention patent publication CN101504006A, the scroll compressor in this solution makes the volume of the compression chamber change by the meshing of the moving and static scroll disks, but the curve surface of the scroll disk has high requirements for machining accuracy and strict requirements for alignment technology. The rolling rotor compressor is a common compressor in air-conditioning systems, especially widely used in small and medium-sized air conditioners, but it has some inherent defects in its structure. For example, in the "pump body assembly of a rotor compressor, rotor compressor and air conditioner" disclosed in Chinese utility model patent CN211819906U, when the main shaft rotates once, the suction and exhaust cycle is completed once, the suction and exhaust are discontinuous, the gas pressure fluctuates greatly, and this solution requires reed pieces to separate the cavity, and the vibration of the reed pieces will cause large noise. In addition, in this solution, the rotor and the motor shaft are of the same frequency, and the dynamic friction at the piston end face is relatively large at high speeds.

[0004] In view of the above deficiencies, the present invention proposes an internal meshing gear rotor compressor with large module and few teeth difference, which realizes low-vibration and high-continuity gas compression through special tooth profile design and gas distribution collaborative control. Summary of the Invention

[0005] In order to solve at least one of the problems existing in the prior art, the present invention provides an internal meshing gear rotor compressor with large module and few teeth difference, which solves the problems of large vibration, large noise, and large gas pressure fluctuation of traditional rolling rotor compressors from the motion principle by optimizing the meshing design of the piston and the cylinder and the gas distribution mechanism.

[0006] To achieve the object of the present invention, the present invention provides an internal meshing gear rotor compressor with large module and few teeth difference, including a cylinder and a piston;

[0007] The piston is arranged in the inner cavity of the cylinder. A gear ring with a concave arc tooth profile having z teeth is arranged in the inner cavity of the cylinder. The piston is a planetary gear with a convex arc tooth profile having z - 1 teeth. The tooth difference between the piston and the cylinder is 1, where z is greater than or equal to 2. The piston is meshed and connected with the cylinder;

[0008] While the piston rotates on its own axis, it revolves in the reverse direction around the axis of the cylinder with a radius of eccentricity Δe, and divides the cylinder into z independent compression chambers; When the piston rotates one week on its own axis, each of the z compression chambers successively completes z - 1 times of suction, compression, and exhaust. The revolving speed of the piston is z - 1 times its rotating speed on its own axis.

[0009] Preferably, the radius of the convex arc tooth profile of the piston is the same as the radius of the concave arc tooth profile of the cylinder. The meshing between the cylinder and the piston can be regarded as the internal meshing of a gear ring with an arc tooth profile and a planetary gear.

[0010] Preferably, it further includes a transmission mechanism. The transmission mechanism includes a main shaft. The main shaft passes through the piston. The eccentric part of the main shaft can drive the piston to revolve. The input speed of the main shaft is the same as the revolving speed of the piston.

[0011] Driven by the main shaft, the piston rotates on its own axis and at the same time revolves in the reverse direction around the axis of the cylinder with a radius of eccentricity Δe, and divides the cylinder into z independent compression chambers. There is no gas exchange between the compression chambers.

[0012] Preferably, the transmission mechanism includes an upper bearing support seat and a lower bearing support seat. The main shaft includes an upper eccentric shaft and a lower eccentric shaft which are connected to each other. The upper bearing support seat and the lower bearing support seat are respectively located on both sides of the piston. The lower eccentric shaft rotates in the lower bearing support seat. The upper eccentric shaft rotates in the upper bearing support seat. Both the upper eccentric shaft and the lower eccentric shaft include eccentric sections, and the eccentric sections form an eccentric part to drive the piston to revolve.

[0013] Preferably, the upper eccentric shaft and the lower eccentric shaft form an integral shaft, and both ends are positioned and supported by the upper bearing support seat and the lower bearing support seat. The middle eccentric part drives the piston to perform a revolving motion.

[0014] The upper eccentric shaft and the lower eccentric shaft form an integral shaft. The integral shaft is a sun gear. When the integral shaft rotates one week, the piston rotates in the reverse direction and rotates 1 / (z - 1) week; During one rotation of the shaft, each compression chamber independently completes one suction, compression, and exhaust process.

[0015] Preferably, both the lower bearing support seat and the upper bearing support seat are provided with annular grooves. The annular grooves serve as suction and exhaust buffer spaces.

[0016] Preferably, an exhaust valve plate is installed on the lower bearing support seat to reduce the occurrence of over-compression and under-compression.

[0017] Preferably, it further includes a gas distribution mechanism. There are z - 1 pairs of intake and exhaust channels provided on the piston, and the intake and exhaust channels cooperate with the gas distribution mechanism to realize the intake, compression, and exhaust processes of each compression chamber.

[0018] An air passage is provided on the piston, and gas can flow in the air passage of the piston, enabling each compression chamber to independently complete intake, compression, and exhaust.

[0019] Preferably, the compression ratio is adjusted by changing the length of the intake and exhaust channels on the piston.

[0020] Preferably, the gas distribution mechanism includes an upper gas distribution disk, a lower gas distribution disk, an upper gas distribution chamber, and a lower gas distribution chamber. The upper gas distribution disk and the lower gas distribution disk are symmetrically arranged on both sides of the cylinder, and are respectively in sliding fit with the two end faces of the piston to form a closed compression chamber, and gas grooves are provided on both the upper gas distribution disk and the lower gas distribution disk; the upper gas distribution chamber and the lower gas distribution chamber are respectively arranged on the upper bearing support seat and the lower bearing support seat; the gas in the compression chamber is exchanged through the intake and exhaust channels on the piston and the gas grooves.

[0021] Preferably, the number of the gas grooves is the same as the number of teeth of the cylinder.

[0022] Preferably, the distribution trajectory of the gas grooves coincides with the movement trajectory formed by the intake and exhaust channels during the movement of the piston. When the gas grooves coincide with the intake and exhaust channels on the piston, intake or exhaust of the compression chamber is performed.

[0023] Preferably, the bottom diameter of the teeth of the cylinder is the sum of the top diameter of the teeth of the piston and the eccentricity Δe.

[0024] Preferably, a gas valve is provided on the upper bearing support seat.

[0025] Preferably, the piston is provided with z - 1 pairs of intake and exhaust channels, and both ends of the intake and exhaust channels are respectively on the side surface and the upper surface or the lower surface of the piston.

[0026] Preferably, the tooth profiles of the cylinder and the piston are arc tooth profiles. The outer curved surface of the piston is internally meshed with the inner curved surface of the cylinder in the manner of an arc gear.

[0027] Generally speaking, the present invention has at least the following beneficial effects:

[0028] 1. Through the meshing relationship between the eccentric drive of the main shaft to drive the piston movement and the arc teeth formed by the cylinder, the present invention achieves the effect that when the main shaft rotates one circle, the piston only rotates 1 / (z - 1) circles. At the same main shaft rotation speed, the friction between the upper and lower end faces of the piston can be reduced, effectively extending the service life of the compressor.

[0029] 2. The scroll rotor compressor of the present invention abandons the reed structure in the scroll rotor compressor, greatly reducing the vibration and noise caused by the movement of the slider. At the same time, the number of parts is reduced, the structure is simple, the volume is small, and the equipment failure rate is greatly reduced.

[0030] 3. In the present invention, a closed compression chamber is formed by the piston and the cylinder. During the movement of the piston, each compression chamber independently completes suction, compression, and exhaust, enabling continuous exhaust, reducing gas pulsation, and thus reducing vibration and noise.

[0031] 4. In the present invention, by changing the length of the suction and exhaust channels on the piston surface, the relatively fixed compression ratio can be adjusted according to requirements, thereby adapting to the characteristics of various refrigerants and broadening the applicable range of the compressor for refrigerants. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] In order to more clearly illustrate the technical solutions in the embodiments of the invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings, where:

[0033] Figure 1 is a schematic structural view of the large module and few tooth difference internal meshing gear rotor compressor in the embodiment of the present invention.

[0034] Figure 2 is a schematic side view of the large module and few tooth difference internal meshing gear rotor compressor in the embodiment of the present invention.

[0035] Figure 3 is a front view schematic of the air distribution disk in the embodiment of the present invention.

[0036] Figure 4 is a front view schematic of the piston in the embodiment of the present invention. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0037] In order to make the purpose, technical solutions and advantages of the present invention clearer, the following will further describe the present invention in detail with reference to the drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention. In addition, the technical features involved in the various embodiments of the present invention described below can be combined with each other as long as they do not conflict with each other.

[0038] In addition, in the present invention, descriptions such as "first", "second", etc. are only for descriptive purposes, and do not particularly refer to the meaning of order or sequence, nor are they used to limit the present invention. They are merely used to distinguish components or operations described with the same technical terms, and should not be construed as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features. Thus, features defined with "first", "second" may explicitly or implicitly include at least one such feature. In addition, the technical solutions between various embodiments can be combined with each other, but it must be based on the ability of those of ordinary skill in the art to implement. When the combination of technical solutions results in contradictions or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0039] Please refer to Figure 1 , a large-module, few-tooth-difference internal meshing gear rotor compressor provided by an embodiment of the present invention includes a cylinder 7 and a piston 14 disposed inside the large-module, few-tooth-difference internal meshing gear rotor compressor. The piston 14 is disposed in the inner cavity of the cylinder 7. The cross-section of the inner cavity of the cylinder 7 is a concave circular arc tooth profile gear ring with z teeth, and the cross-section of the piston 14 is a convex circular arc tooth profile planetary gear with z - 1 teeth, where z is an even number greater than or equal to 2. The outer surface of the piston 14 is internally meshed with the inner surface of the cylinder 7 in the manner of an arc gear. The piston 14 divides the cylinder 7 into z independent compression chambers 6.

[0040] During operation, while the piston 14 rotates on its own axis, it revolves in the reverse direction around the axis of the cylinder 7 with a radius of eccentricity Δe. When the piston 14 rotates one week, each of the z compression chambers 6 independently completes z - 1 times of suction, compression, and exhaust. The revolving speed of the piston 14 is z - 1 times the rotation speed of the piston 14 on its own axis, and the revolving speed of the piston 14 is consistent with the main shaft rotation speed. Here, the eccentricity Δe is the eccentricity of the parallel deviation between the axis of the piston 14 and the axis of the cylinder 7.

[0041] There are z - 1 pairs of suction and exhaust channels provided inside the piston 14, and the number of pairs of the suction and exhaust channels is equal to the number of teeth of the piston 14.

[0042] In one embodiment of the present invention, the compressor further includes a transmission mechanism and a gas distribution mechanism disposed within the compressor. The transmission mechanism includes an upper eccentric shaft 1, an upper bearing support seat 2, a lower eccentric shaft 12, and a lower bearing support seat 10; the upper eccentric shaft 1 is connected to the lower eccentric shaft 12 to form a complete eccentric shaft, which sequentially passes through the upper bearing support seat 2, the piston 14, and penetrates into the lower bearing support seat 10. The upper eccentric shaft 1 and the lower eccentric shaft 12 form an integral shaft, and both ends are positioned and supported by the upper bearing support seat 2 and the lower bearing support seat 10. Both the upper eccentric shaft 1 and the lower eccentric shaft 12 include eccentric segments, and the eccentric portions formed in the middle of the eccentric segments drive the piston 14 to perform a revolution motion; the piston 14 is coaxially arranged with the eccentric shaft, and the axis of the piston 14 is parallel to and has a distance from the axis of the cylinder, and the distance is the eccentricity Δe. The integral shaft is the sun gear, and the piston 14 rotates in the reverse direction by 1 / (z - 1) turns when the integral shaft rotates one week. The compression chamber 6 independently completes one suction, compression, and exhaust process respectively during one rotation of the shaft; the gas distribution mechanism includes an upper gas distribution disk 4, an upper gas distribution chamber 3, a lower gas distribution disk 9, and a lower gas distribution chamber 11; the upper gas distribution disk 4 and the lower gas distribution disk 9 are symmetrically arranged on both sides of the cylinder 7 and are respectively located inside the upper bearing support seat 2 and the lower bearing support seat 10. The upper gas distribution disk 4 and the lower gas distribution disk 9 are respectively in sliding fit with the two end faces of the piston 14. The structures of the upper gas distribution disk 4 and the lower gas distribution disk 9 are the same. Please refer to Figure 1 and Figure 3 , both the upper gas distribution disk 4 and the lower gas distribution disk 9 are provided with gas grooves 16 with a plurality of long circular holes in the circumferential direction, and the number of the gas grooves 16 corresponds to the number of the compression chambers 6; the upper gas distribution chamber 3 is disposed on the upper bearing support seat 2, and the lower gas distribution chamber 11 is disposed on the lower bearing support seat 10; the gas grooves 16 communicate with the upper gas distribution chamber 3 and the lower gas distribution chamber 11 on the upper bearing support seat 2 and the lower bearing support seat 10, and the upper gas distribution chamber 3 and the lower gas distribution chamber 11 are communicated with the compression chamber 6 in the cylinder 7 through the gas grooves 16 and the suction and exhaust channels (8, 13). The gas distribution disk and the piston 14 cooperate with each other to complete the suction, compression, and exhaust actions.

[0043] In one embodiment of the present invention, the compressor further includes a gas valve 17, and the gas valve 17 is disposed on the upper bearing support seat 2.

[0044] In one embodiment of the present invention, annular grooves are provided on both the lower bearing support seat 10 and the upper bearing support seat 2, and the annular grooves can be used as suction and exhaust buffer spaces. An exhaust valve plate is further installed on the lower bearing support seat 10 to reduce the occurrence of over-compression and under-compression.

[0045] In one embodiment of the present invention, the bottom radius of the teeth of the cylinder 7 is the sum of the top radius of the teeth of the piston 14 and the eccentricity Δe.

[0046] In one embodiment of the present invention, as Figure 2 shown, a large module, few tooth difference internal meshing gear rotor compressor with z = 3 is provided. The piston 14 is a planet gear with 2 teeth, and the cylinder 7 is a gear ring with 3 teeth. Two pairs of suction and exhaust channels are formed at the tooth surface to the end face of the piston 14. The piston 14 divides the cylinder 7 into three independent compression chambers 6. When the piston 14 rotates one revolution, each of the three compression chambers 6 successively completes 2 times of suction, compression and exhaust. Further explanation, the revolution speed of the piston 14 is 2 times the rotation speed, and the input speed of the compressor main shaft composed of the upper eccentric shaft 1 and the lower eccentric shaft 12 is the same as the revolution speed of the piston 14.

[0047] Specifically, as Figure 4 shown, the two pairs of suction and exhaust channels are the first suction and exhaust channel 5, the second suction and exhaust channel 8, the third suction and exhaust channel 13 and the fourth suction and exhaust channel 15 respectively. The first suction and exhaust channel 5 and the second suction and exhaust channel 8 are a pair and are symmetrically arranged along the center of the piston 14. The third suction and exhaust channel 13 and the fourth suction and exhaust channel 15 are a pair and are symmetrically arranged along the center of the piston 14.

[0048] Further explanation, in one embodiment of the present invention, a large module, few tooth difference internal meshing gear rotor compressor with z = 3 is provided, and its working process is as follows: The piston 14 rotates within the cylinder 7 while revolving in the reverse direction around the axis of the cylinder 7 with a radius of eccentricity Δe, driving the two pairs of suction and exhaust channels (the first suction and exhaust channel 5, the second suction and exhaust channel 8 and the third suction and exhaust channel 13, the fourth suction and exhaust channel 15) on it to communicate with the air grooves 16 on the two side air distribution plates (the upper air distribution plate 4 and the lower air distribution plate 9) respectively, and respectively completing the suction, compression and exhaust of each compression chamber 6. One side of the two pairs of suction and exhaust channels is the suction air channel and the other side is the exhaust air channel. When the rotation direction of the piston 14 is opposite, the direction of the suction and exhaust channels also reverses. Driven by the cylinder 7 meshing restriction and the eccentric shaft, the piston 14 makes a movement of both rotating and revolving in the reverse direction around the cylinder, and the revolution speed is 2 times the rotation speed. When the piston 14 rotates one revolution, each of the three compression chambers 6 successively completes two times of suction, compression and exhaust.

[0049] In one embodiment of the present invention, by adjusting the eccentricity Δe and the gear modulus, different compression ratios and refrigerating capacities can be obtained, so as to be applicable to different types of refrigerants and refrigeration requirements.

[0050] It is easy for those skilled in the art to understand that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent replacements and improvements made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A large module, few tooth difference internal meshing gear rotor compressor, characterized in that, It includes a cylinder (7) and a piston (14); The piston (14) is arranged in the inner cavity of the cylinder (7). A gear ring with a concave arc tooth profile having z teeth is arranged in the inner cavity of the cylinder (7). The piston (14) is a planetary gear with a convex arc tooth profile having z - 1 teeth. The tooth difference between the piston (14) and the cylinder (7) is 1, where z is greater than or equal to 2. The piston (14) is meshed and connected with the cylinder (7); While the piston (14) rotates on its own axis, it revolves in the reverse direction around the axis of the cylinder (7) with a radius of eccentricity Δe, and divides the cylinder (7) into z independent compression chambers (6). The revolving speed of the piston (14) is z - 1 times its self - rotation speed; when the piston (14) rotates one week, each of the z compression chambers (6) successively completes z - 1 times of intake, compression, and exhaust.

2. A large module, few tooth difference internal meshing gear rotor compressor according to claim 1, characterized in that, It further includes a transmission mechanism. The transmission mechanism includes a main shaft. The main shaft passes through the piston (14), and the eccentric part of the main shaft can drive the piston (14) to revolve. The input speed of the main shaft is the same as the revolving speed of the piston (14).

3. A large modulus, few tooth difference internal meshing gear rotor compressor according to claim 2, characterized in that, The transmission mechanism includes an upper bearing support seat (2) and a lower bearing support seat (10). The main shaft includes an upper eccentric shaft (1) and a lower eccentric shaft (12) which are connected to each other. The upper bearing support seat (2) and the lower bearing support seat (10) are respectively located on both sides of the piston (14). The lower eccentric shaft (12) rotates and is located in the lower bearing support seat (10). The upper eccentric shaft (1) is rotatably arranged in the upper bearing support seat (2). Both the upper eccentric shaft (1) and the lower eccentric shaft (12) include eccentric segments, and the eccentric segments form eccentric parts to drive the piston (14) to revolve.

4. A large module, few tooth difference internal meshing gear rotor compressor according to claim 3, characterized in that Both the lower bearing support seat (10) and the upper bearing support seat (2) are provided with annular grooves.

5. A large module, few tooth difference internal meshing gear rotor compressor according to claim 3, characterized in that It further includes a gas distribution mechanism. The piston (14) is provided with z - 1 pairs of intake and exhaust channels. The intake and exhaust channels cooperate with the gas distribution mechanism to realize the intake, compression, and exhaust processes of each compression chamber (6).

6. A large modulus, few tooth difference internal meshing gear rotor compressor according to claim 5, characterized in that The compression ratio is adjusted by changing the length of the intake and exhaust channels on the piston (14).

7. A large module, few tooth difference internal meshing gear rotor compressor according to claim 5, characterized in that The gas distribution mechanism includes an upper gas distribution disk (4), a lower gas distribution disk (9), an upper gas distribution chamber (3), and a lower gas distribution chamber (10). The upper gas distribution disk (4) and the lower gas distribution disk (9) are respectively arranged on both sides of the cylinder (7) and are respectively in sliding fit with the two end faces of the piston (14), and both the upper gas distribution disk (4) and the lower gas distribution disk (9) are provided with gas grooves (16); the upper gas distribution chamber (3) and the lower gas distribution chamber (11) are respectively arranged on the upper bearing support seat (2) and the lower bearing support seat (10); the compression chamber (6) conducts gas exchange through the intake and exhaust channels on the piston (14) and the gas grooves (16).

8. A large module, few tooth difference internal meshing gear rotor compressor according to claim 7, characterized in that The number of the gas grooves (16) is the same as the number of teeth of the cylinder (7).

9. A large module, few tooth difference internal meshing gear rotor compressor according to claim 8, characterized in that The distribution track of the gas grooves (16) coincides with the movement track formed by the intake and exhaust channels when the piston (14) moves.

10. A large modulus, few tooth difference internal meshing gear rotor compressor according to any one of claims 1-9, characterized in that, The bottom diameter of the teeth of the cylinder (7) is the sum of the top diameter of the piston (14) and the eccentricity Δe.

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