Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment, and relates to the technical field of refrigeration equipment, the compressor comprises a shell, and a crankshaft, a first bearing, a first cylinder, a second cylinder, a second bearing, a first silencer and a second silencer which are arranged in the shell; the first air cylinder and the shell form a compression cavity. The first silencer is installed on the first bearing and communicates with the first air cylinder and the compression cavity. The second silencer is mounted on the second bearing, and the second silencer communicates with the compression cavity through an exhaust channel; the first bearing, the second air cylinder and the second bearing penetrate through the exhaust channel, and the exhaust channel is isolated from the first silencer. According to the technical scheme, the exhaust pressure pulsation of the compressor is improved, and 3f noise and axial vibration are reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of refrigeration equipment, in particular to a compressor and refrigeration equipment using the compressor. Background Art

[0002] During operation, high-pressure gas is trapped within the casing of a rotary compressor. To reduce exhaust pressure pulsation and noise, a muffler is typically installed. Currently, exhaust noise reduction is mostly achieved through exhaust mufflers. However, due to the cavity structure of the muffler, the cavity mode is already defined, making it impossible to eliminate the trough noise.

[0003] Therefore, it is necessary to design a compressor that can effectively improve the exhaust pressure pulsation of the compressor and reduce 3f noise and axial vibration. Utility Model Content

[0004] The main purpose of the utility model is to provide a compressor, the purpose of which is to improve the exhaust pressure pulsation of the compressor and reduce 3f noise and axial vibration.

[0005] To achieve the above-mentioned object, the present invention provides a compressor comprising a housing and a crankshaft, a first bearing, a first cylinder, a second cylinder, and a second bearing disposed in the housing; the first cylinder and the housing form a compression chamber, and further comprising:

[0006] a first muffler, mounted on the first bearing and in communication with the first cylinder and the compression chamber;

[0007] a second muffler mounted on the second bearing, the second muffler being in communication with the compression chamber through an exhaust passage;

[0008] The exhaust passage passes through the first bearing, the second cylinder and the second bearing, and the exhaust passage is isolated from the first muffler.

[0009] In one embodiment, the exhaust passage has a first flow port arranged on the first bearing; the compressor also includes an oil deflector cap, which is installed on the first bearing and covers the first flow port, and the oil deflector cap has a first exhaust port facing the side wall of the shell.

[0010] In one embodiment, the exhaust passage has a first flow port provided on the first bearing; the first muffler has a flange edge for being mounted on the first bearing; the position of the flange edge facing the first flow port is recessed toward a side away from the first flow port to form an oil deflector cap; the oil deflector cap has a first exhaust port facing the side wall of the shell.

[0011] In one embodiment, the oil deflector cap is arc-shaped.

[0012] In one embodiment, there are two oil deflector caps, and a central angle formed by the two oil deflector caps and the axis of the first muffler is in a range of 70°-100°.

[0013] In one embodiment, a cross-sectional area of ​​the first exhaust port is 0.8-1.2 times a cross-sectional area of ​​the first flow port.

[0014] In one embodiment, the first muffler has two second exhaust ports, the number of the first exhaust ports is two, and the central angle formed by the two first exhaust ports and the axis of the first muffler is inside the central angle formed by the two second exhaust ports and the axis of the first muffler.

[0015] In one embodiment, a central angle formed by the two second exhaust ports and the axis of the first muffler is in a range of 90° to 170°.

[0016] In one embodiment, the first muffler, the first bearing, the first cylinder, the second cylinder, the second bearing, and the second muffler are sequentially sleeved on the crankshaft from top to bottom.

[0017] The utility model also provides a refrigeration device, comprising the above-mentioned compressor.

[0018] The compressor of the technical solution of the present invention adopts two channels to transport high-temperature and high-pressure gas; in the first channel, the high-temperature and high-pressure refrigerant generated by the first cylinder is transmitted from the first muffler to the compression chamber; in the second side channel, the high-temperature and high-pressure refrigerant generated by the second cylinder is transmitted from the second muffler to the compression chamber through the exhaust channel running through the first bearing, the second bearing and the second cylinder, thereby improving the exhaust pressure pulsation of the compressor and reducing 3f noise and axial vibration. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0020] Figure 1 A partial structural diagram of an embodiment of a compressor provided by the utility model;

[0021] Figure 2 A schematic cross-sectional view of an exhaust passage of a compressor according to the present invention;

[0022] Figure 3This is another schematic cross-sectional view of an embodiment of a compressor provided by the present invention;

[0023] Figure 4 A schematic structural diagram of a first muffler of an embodiment of a compressor provided by the present utility model from one perspective;

[0024] Figure 5 A schematic structural diagram of a first muffler of an embodiment of a compressor provided by the present utility model from another perspective;

[0025] Figure 6 This is a comparison diagram of noise verification at different frequencies of an embodiment of the compressor provided by the present invention;

[0026] Figure 7 This is a comparison diagram of axial vibration verification of an embodiment of the compressor provided by the present invention.

[0027] Description of Figure Numbers:

[0028] 100. Compressor; 10. First muffler; 11. Second exhaust port; 12. Flange edge; 20. Crankshaft; 30. Second muffler; 40. First cylinder; 41. Second flow port; 50. Second cylinder; 51. Third flow port; 60. First bearing; 61. First flow port; 62. First exhaust valve plate; 70. Second bearing; 71. Fourth flow port; 72. Second exhaust valve plate; a. Exhaust channel; 80. Oil deflector cap; 81. First exhaust port; 90. Motor. DETAILED DESCRIPTION

[0029] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only 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 ordinary technicians in this field without making any creative work are within the scope of protection of the present invention.

[0030] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement status, etc. between the components in a certain specific posture. If the specific posture changes, the directional indications will also change accordingly.

[0031] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present invention, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features limited to "first" and "second" may explicitly or implicitly include at least one of such features. In addition, if "and / or" or "and / or" appears in the full text, its meaning includes three parallel schemes. Taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme in which A and B are satisfied at the same time. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the fact that ordinary technicians in this field can implement it. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0032] During operation, rotary compressors contain high-pressure gas within their casings. To reduce exhaust pressure pulsation and noise, they are typically equipped with mufflers. Currently, most compressors use exhaust mufflers to reduce exhaust noise. However, due to the cavity structure of the muffler, the cavity mode is already defined, making it difficult to eliminate low-pitched noise, especially the relatively large 3f noise and axial vibration.

[0033] Therefore, it is necessary to effectively improve the exhaust pressure pulsation of the compressor and reduce 3f noise and axial vibration.

[0034] Please refer to Figure 1 and Figure 2As shown, a compressor 100 provided by one embodiment of the present application includes a shell (not shown in the figure), a first muffler 10, a crankshaft 20, a second muffler 30, a first cylinder 40, a second cylinder 50, a first bearing 60 and a second bearing 70. The first muffler 10, the crankshaft 20, the second muffler 30, the first cylinder 40, the second cylinder 50, the first bearing 60 and the second bearing 70 are all installed in the shell. The first cylinder 40 and the shell form a compression chamber. The shell is arranged outside the first muffler 10, the crankshaft 20, the second muffler 30, the first cylinder 40, the second cylinder 50, the first bearing 60 and the second bearing 70, and the side wall of the shell abuts against the outer surface of the cylinder body of the first cylinder 40 to form the compression chamber between the shell and the first cylinder 40, and the compression chamber is used to receive the high-temperature and high-pressure refrigerant sent from the first cylinder 40 and the second cylinder 50. The first and second cylinders 40 and 50 are used to draw low-temperature refrigerant from the outside through corresponding pipes and compress the low-temperature refrigerant. Driven by the motor 90, the crankshaft 20 rotates, which in turn drives the rotors of the first and second cylinders 40 and 50, thereby compressing the refrigerant within the cylinders of the first and second cylinders 40 and 50 to generate high-temperature, high-pressure refrigerant. After the pressure within the first and second cylinders 40 and 50 reaches a certain value, the high-temperature, high-pressure refrigerant within the first and second cylinders 40 and 50 first passes through the first and second mufflers 10 and 30 before being delivered to the compression chamber.

[0035] The first muffler 10 is mounted on the first bearing 60, and the first cylinder 40 is connected to the first muffler 10 and the compression chamber to deliver the high-temperature, high-pressure gas generated by the first cylinder 40 to the compression chamber. The first muffler 10 has a second exhaust port 11, through which the refrigerant in the first muffler 10 flows into the compression chamber. The second muffler 30 is mounted on the second bearing 70, and is connected to the compression chamber via the exhaust channel a. The second muffler 30 is connected to the second cylinder 50, and the high-temperature, high-pressure gas generated by the second cylinder 50 is first transmitted to the second muffler 30, then passes through the exhaust channel a, and is finally delivered to the compression chamber. In this embodiment, the exhaust channel a passes through the second cylinder 50, the first bearing 60, and the second bearing 70, and the exhaust channel a is isolated from the first muffler 10. It should be noted that the first muffler 10 and the second muffler 30 are both cavity structures, and both are used for silencer.

[0036] Compressors on the market typically have an upper and lower muffler connected. This means that the high-temperature, high-pressure gas generated by the lower cylinder is also sent to the upper muffler, and then from the upper muffler to the compression chamber. This structure, where the high-temperature, high-pressure gas generated by both the upper and lower cylinders is discharged through the upper muffler, can cause excessive internal pressure, exciting cavity modes and failing to eliminate low-frequency noise, especially 3f noise. Furthermore, axial vibration is also significant. 3f noise is a 250Hz frequency noise.

[0037] This application uses two channels to transport high-temperature and high-pressure gas; in the first channel, the high-temperature and high-pressure refrigerant generated by the first cylinder 40 is transmitted from the first muffler 10 to the compression chamber; in the second bypass channel, the high-temperature and high-pressure refrigerant generated by the second cylinder 50 is transmitted from the second muffler 30 to the compression chamber through the exhaust channel a that passes through the first bearing 60, the second bearing 70 and the second cylinder 50. This application sends high-temperature and high-pressure gas to the compression chamber through two channels, which can reduce 3f noise and reduce axial vibration. Figure 6 As shown in the figure, the noise at 250HZ is reduced by 5.6dB. Figure 7 As shown, the axial vibration at 3f is improved by 69%.

[0038] Please refer to Figure 2 As shown, in an optional embodiment, the exhaust passage a has a first flow opening 61 provided on the first bearing 60. The compressor 100 further includes an oil deflector cap 80, which is mounted on the first bearing 60 and covers the first flow opening 61. The oil deflector cap 80 has a first exhaust port 81, which is provided toward the side wall of the housing.

[0039] Specifically, the exhaust channel a has a first flow port 61, a second flow port 41, a third flow port 51, and a fourth flow port 71. The first flow port 61 is provided on the first bearing 60, the second flow port 41 is provided at the edge of the cylinder body of the first cylinder 40, the third flow port 51 is provided at the edge of the cylinder body of the second cylinder 50, and the third flow port 51 is provided on the second bearing 70. The first flow port 61, the first flow port 61, the second flow port 41, the third flow port 51, and the fourth flow port 71 are all provided opposite each other, and the fourth flow port 71 is directly connected to the second muffler 30. The high-temperature and high-pressure gas in the second cylinder 50 flows into the second muffler 30, then passes through the exhaust channel a (i.e., the first flow port 61, the second flow port 41, the third flow port 51, and the fourth flow port 71), and is then delivered to the compression chamber. The compressor 100 of the present application also includes an oil deflector cap 80, which is mounted on the first bearing 60 and has a first exhaust port 81 on the oil deflector cap 80, and the first exhaust port 81 is arranged toward the side wall of the shell. In the present embodiment, the first muffler 10, the first bearing 60, the first cylinder 40, the second cylinder 50, the second bearing 70 and the second muffler 30 are sequentially sleeved on the crankshaft 20 from top to bottom. The crankshaft 20 is vertically arranged, and the exhaust channel a is vertically arranged, so the refrigerant gas and lubricating oil mixture in the second cylinder 50 will be directly discharged upward along the exhaust channel a in the vertical direction. The present application sets an oil deflector cap 80 above the exhaust channel a, and the oil deflector cap 80 covers the first flow port 61, and the first exhaust port 81 is arranged in the horizontal direction, that is, the refrigerant gas and lubricating oil mixture in the second cylinder 50 will first hit the oil deflector cap 80, and the oil deflector cap 80 plays a separation role, which can prevent part of the lubricating oil from being discharged.

[0040] When the lubricating oil of the compressor on the market passes over the exhaust hole of the muffler, the discharged refrigerant gas is mixed with the lubricating oil and directly discharged outside the shell, thereby increasing the oil discharge of the compressor. If it runs for a long time, the risk of lubricating oil reduction increases. The present application is provided with an oil shielding cap 80, and the oil shielding cap 80 covers the first flow port 61, that is, the oil shielding cap 80 covers the exhaust channel a, the exhaust channel a is vertically arranged, and the second exhaust hole is arranged in the horizontal direction. When the refrigerant gas and lubricating oil mixture of the second cylinder 50 is transmitted to the oil shielding cap 80, part of the lubricating oil will be blocked by the oil shielding cap 80, and the refrigerant gas can be sent to the compression chamber from the second exhaust hole on the side. Therefore, the present application can reduce the oil discharge of the compressor 100.

[0041] Please refer to Figure 2 and Figure 4As shown, in an optional embodiment, the first muffler 10 has a flange 12, which is used to mount the first bearing 60. The flange 12 is recessed toward a side away from the first flow port 61 at a position opposite the first flow port 61 to form an oil deflector cap 80, which has a first exhaust port 81 facing the side wall of the housing.

[0042] Specifically, the first muffler 10 has a flange 12, which fits the first bearing 60, and a locking bolt passes through the flange 12 and the first bearing 60 to fix the first muffler 10 on the first bearing 60. The oil deflector cap 80 and the first muffler 10 are an integrally formed structure. The oil deflector cap 80 is arranged on the flange 12, and the flange 12 is recessed toward the side away from the first circulation port 61 to form an oil deflector cap 80 with a concave cavity structure. The oil deflector cap 80 covers the first circulation port 61, and a first exhaust port 81 is also provided on the oil deflector cap 80 for the refrigerant to pass through. The first exhaust port 81 faces the side wall of the shell, and the shell is arranged vertically, that is, the side wall of the shell is in the vertical direction, and the first exhaust port 81 is arranged in the horizontal direction. The exhaust channel a is arranged in the vertical direction, so the high-temperature and high-pressure refrigerant and lubricating oil will follow the exhaust channel a. Before passing through the first exhaust port 81, part of the lubricating oil will be blocked by the oil baffle cap 80, thereby reducing the oil discharge amount of the compressor 100.

[0043] Please refer to Figure 4 As shown, in an optional embodiment, the shape of the oil deflector cap 80 is set to be arc-shaped.

[0044] Specifically, the second cylinder 50 transmits the compressed high-temperature and high-pressure refrigerant to the oil deflector cap 80 through the exhaust channel a, and then transmits the refrigerant to the compression chamber through the first exhaust port 81. Therefore, the oil deflector cap 80 is always in a high-temperature and high-pressure space. The oil deflector cap 80 is set to be arc-shaped in order to reduce the problem of stress concentration on the oil deflector cap 80, increase the pressure resistance of the oil deflector cap 80, and thus improve the service life of the oil deflector cap 80. The surface of the oil deflector cap 80 in this embodiment is a curved surface structure and does not have a right-angle surface structure.

[0045] In this embodiment, there are two oil deflector caps 80. The central angle formed by the two oil deflector caps 80 and the axis of the first muffler 10 is in the range of 70-100. The cross-sectional area of ​​the first exhaust port 81 is 0.8-1.2 times the cross-sectional area of ​​the first flow port 61.

[0046] like Figure 5As shown, specifically, the number of the oil deflector caps 80 is set to two, that is, the number of the exhaust channels a is also set to two. The oil deflector caps 80 correspond to the exhaust channels a one-to-one. An angle α is formed between the two oil deflector caps 80 and the first muffler 10, and the range of α is 70°-100°. The two oil deflector caps 80 are set in a smaller range, that is, the two first exhaust ports 81 are set in a smaller range, so as to avoid the symmetry of the two first exhaust ports 81, and thus avoid the occurrence of resonance. The cross-sectional area of ​​the first exhaust port 81 is 0.8-1.2 times the cross-sectional area of ​​the first circulation port 61. After testing, when the ratio of the cross-sectional area of ​​the first exhaust port 81 to the cross-sectional area of ​​the first circulation port 61 is 0.8-1.2, the silencing effect is better.

[0047] There are two second exhaust ports 11, that is, each oil deflector cap 80 is provided with a second exhaust port 11, and the central angle formed by the two first exhaust ports 81 and the axis of the first muffler 10 is on the inner side of the central angle formed by the two second exhaust ports 11 and the axis of the first muffler 10.

[0048] For details, please refer to Figures 3 to 5 As shown, the angle formed between the two first exhaust ports 81 and the first muffler 10 is α, and the central angle formed between the two second exhaust ports 11 and the axis of the first muffler 10 is β, where α<β. That is, the two first exhaust ports 81 and the two second exhaust ports 11 are arranged on the same semicircular side of the first muffler 10. A first exhaust valve plate 62 is also provided on the first bearing 60. The first exhaust valve plate 62 is a one-way valve. When the pressure in the first cylinder 40 reaches a certain value, the first exhaust valve plate 62 opens to release the high-pressure refrigerant in the first cylinder 40 into the first muffler 10, where it is silenced through the cavity in the first muffler 10. Similarly, a second exhaust valve plate 72 is also provided on the second bearing 70. The first exhaust valve plate 62 and the second exhaust valve plate 72 are on the same semicircular side of the first muffler 10, and the first exhaust valve plate 62, the second exhaust valve plate 72 and the second exhaust port 11 and the first exhaust port 81 are respectively located on different semicircular sides. That is, the refrigerant in the first cylinder 40 is drained to lengthen the airflow path, preventing the airflow from directly impacting the second exhaust port 11 on the first muffler chamber, thereby improving the muffler effect. Similarly, the refrigerant in the second cylinder 50 is drained to avoid directly impacting the first exhaust port 81, thereby also improving the muffler effect.

[0049] In this embodiment, the central angle formed by the two second exhaust ports 11 and the axis of the first muffler 10 is in the range of 90°-170°. The present application sets the two second exhaust ports 11 in the range of 90°-170° to make the two second exhaust ports 11 asymmetrical to avoid resonance and to ensure that the distance between the second exhaust ports 11 and the first exhaust port 81 is not too close.

[0050] This application also relates to a refrigeration device that utilizes the aforementioned compressor 100. Compressor 100 utilizes two channels to transport high-temperature, high-pressure gas. In the first channel, high-temperature, high-pressure gas generated by the first cylinder 40 is delivered from the first muffler 10 to the compression chamber. In the second, bypass channel, high-temperature, high-pressure gas generated by the second cylinder 50 is delivered from the second muffler 30 to the compression chamber via the exhaust channel a that passes through the first bearing 60, the second bearing 70, and the second cylinder 50. This reduces 3f noise and axial vibration.

[0051] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. All equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect application in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A compressor comprising a housing and a crankshaft, a first bearing, a first cylinder, a second cylinder, and a second bearing disposed in the housing; the first cylinder and the housing form a compression chamber, characterized in that: Also includes: a first muffler, mounted on the first bearing and in communication with the first cylinder and the compression chamber; a second muffler mounted on the second bearing, the second muffler being in communication with the compression chamber through an exhaust passage; The exhaust passage passes through the first bearing, the second cylinder and the second bearing, and the exhaust passage is isolated from the first muffler.

2. The compressor according to claim 1, wherein The exhaust passage has a first flow port arranged on the first bearing; the compressor also includes an oil deflector cap, which is installed on the first bearing and covers the first flow port, and the oil deflector cap has a first exhaust port facing the side wall of the shell.

3. The compressor according to claim 1, wherein The exhaust passage has a first flow port arranged on the first bearing; the first muffler has a flange edge for being installed on the first bearing; the position of the flange edge facing the first flow port is recessed toward the side away from the first flow port to form an oil deflector cap; the oil deflector cap has a first exhaust port facing the side wall of the shell.

4. The compressor according to claim 2 or 3, characterized in that The shape of the oil deflector cap is arc-shaped.

5. The compressor according to claim 2 or 3, characterized in that There are two oil deflector caps, and the central angle formed by the two oil deflector caps and the axis of the first muffler is in the range of 70°-100°.

6. The compressor according to claim 2 or 3, characterized in that The cross-sectional area of ​​the first exhaust port is 0.8-1.2 times the cross-sectional area of ​​the first flow port.

7. The compressor according to claim 5, wherein The first muffler has two second exhaust ports, and the number of the first exhaust ports is two; the central angle formed by the two first exhaust ports and the axis of the first muffler is inside the central angle formed by the two second exhaust ports and the axis of the first muffler.

8. The compressor according to claim 7, wherein The central angle formed by the two second exhaust ports and the axis of the first muffler is in the range of 90°-170°.

9. The compressor according to claim 1, wherein The first muffler, the first bearing, the first cylinder, the second cylinder, the second bearing and the second muffler are sequentially sleeved on the crankshaft from top to bottom.

10. A refrigeration device, characterized in that: Comprising the compressor according to any one of claims 1 to 9.

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