Compressor and refrigeration apparatus

Abstract

The application discloses a compressor and a refrigeration equipment, wherein the compressor comprises a shell, a crankcase, a first silencer and a first sealing cover, the crankcase is installed in the shell, the crankcase has a cylinder cavity, a first high-pressure cavity and a first overflow hole, the first overflow hole is configured to communicate the cylinder cavity and the first high-pressure cavity, the first sealing cover covers an opening of the first high-pressure cavity, the first silencer is arranged in the first high-pressure cavity, an outer peripheral wall of the first silencer and an inner peripheral wall of the first high-pressure cavity jointly define a first silencing space, an inner peripheral wall of the first silencer, the first sealing cover and a bottom wall of the first high-pressure cavity jointly form a second silencing space, the first silencer is provided with a first air inlet hole, the first silencing space is communicated with the second silencing space through the first air inlet hole, and the refrigerant is damped in the first silencing space and the second silencing space respectively when the compressor discharges, so that two-stage damping can be performed on the refrigerant, the exhaust pulsation is reduced, and vibration noise is reduced.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0002] With the continuous development of society and the gradual improvement of people's living standards, the requirements for refrigerator noise levels are also increasing. As the main source of refrigerator noise, the compressor faces higher demands for its noise performance. Generally speaking, noise is divided into aerodynamic noise, mechanical noise, and electromagnetic noise. Among aerodynamic noise, the vibration noise generated during compressor exhaust accounts for a large proportion. Therefore, reducing the vibration generated during exhaust can effectively reduce exhaust noise. Existing compressors still produce significant exhaust pulsations during operation, resulting in considerable noise from the refrigeration equipment. Summary of the Invention

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes a compressor capable of reducing exhaust pulsation, thereby reducing vibration noise.

[0004] The present invention also proposes a refrigeration device having the above-mentioned compressor.

[0005] According to a first embodiment of the compressor of the present invention, the compressor includes:

[0006] case;

[0007] A crankcase, installed within the housing, the crankcase having a cylinder chamber, a first high-pressure chamber, and a first flow passage, the first flow passage being configured to connect the cylinder chamber and the first high-pressure chamber;

[0008] The first sealing cap is placed over the opening of the first high-pressure chamber;

[0009] A first silencing component is disposed within the first high-pressure chamber. The outer peripheral wall of the first silencing component and the inner peripheral wall of the first high-pressure chamber together define a first silencing space. The lower end of the peripheral wall of the first silencing component abuts against the bottom wall of the first high-pressure chamber, and the upper end of the peripheral wall of the first silencing component abuts against the first sealing cover. The inner peripheral wall of the first silencing component, the first sealing cover, and the bottom wall of the first high-pressure chamber enclose a second silencing space. The first silencing component is provided with a first air inlet, and the first silencing space is connected to the second silencing space through the first air inlet.

[0010] The compressor according to an embodiment of the present invention has at least the following beneficial effects:

[0011] When the compressor discharges, the refrigerant flows through the cylinder cavity, the first flow hole, the first silencer space, the first intake hole, and the second silencer space. The refrigerant is silenced in the first silencer space and the second silencer space respectively, which can perform two-stage silencer to reduce exhaust pulsation and vibration noise.

[0012] According to some embodiments of the present invention, the first silencer includes a first cylinder and a first flange. The first air inlet is disposed on the first cylinder along the axial direction of the first cylinder. The first flange is disposed at one end of the first cylinder near the first sealing cover. The first flange is arranged around the outer peripheral wall of the first cylinder. The first flange is sandwiched between the end wall of the first high-pressure chamber facing the opening and the first sealing cover.

[0013] According to some embodiments of the present invention, a first gasket is provided between the first flange and the first sealing cover, and / or a second gasket is provided between the end wall of the first high-pressure chamber facing the opening and the first flange.

[0014] According to some embodiments of the present invention, the minimum wall thickness of the first cylinder is T1, which satisfies: 1mm≤T1≤3mm.

[0015] According to some embodiments of the present invention, along the axial direction of the first cylinder, the minimum thickness of the first flange is T2, which satisfies: 1mm≤T2≤2mm.

[0016] According to some embodiments of the present invention, the bottom wall of the first high-pressure chamber is provided with a first protrusion, the first sealing cover is connected to the first protrusion by a first fastener, the first cylinder is sleeved on the outer periphery of the first protrusion, and the lower end of the first cylinder is in sealing contact with the bottom wall of the first high-pressure chamber.

[0017] According to some embodiments of the present invention, the minimum inner diameter of the first silencing component is D1, which satisfies the following condition: 7mm≤D1≤10mm.

[0018] According to some embodiments of the present invention, the compressor further includes a first exhaust pipe, one end of which passes through the first sealing cover and extends into the second silencing space.

[0019] According to some embodiments of the present invention, the crankcase has a second high-pressure chamber and a second flow passage. A second silencing component is provided in the second high-pressure chamber. The crankcase is provided with a second sealing cover, which seals the opening of the second high-pressure chamber. The first silencing component is provided with an air outlet through its peripheral wall. The inner peripheral wall of the second high-pressure chamber and the outer peripheral wall of the second silencing component together define a third silencing space. The second flow passage is configured to connect the first silencing space and the third silencing space. The lower end of the peripheral wall of the first silencing component abuts against the bottom wall of the second high-pressure chamber, and the upper end of the peripheral wall of the first silencing component abuts against the second sealing cover. The inner peripheral wall of the second silencing component, the second sealing cover, and the bottom wall of the second high-pressure chamber enclose a fourth silencing space. The second silencing component is provided with a second air inlet, and the third silencing space is connected to the fourth silencing space through the second air inlet.

[0020] According to some embodiments of the present invention, the first air inlet is located on the side of the first muffler near the first flow outlet.

[0021] According to some embodiments of the present invention, the first air inlet and the air outlet are offset from each other along the circumference of the first muffler.

[0022] According to some embodiments of the present invention, the compressor further includes a second exhaust pipe, one end of which passes through the second sealing cover and extends into the fourth silencing space.

[0023] The refrigeration equipment according to the third embodiment of the present invention includes the compressor described in the above embodiments.

[0024] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0025] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0026] Figure 1 This is an exploded view of the compressor according to the first embodiment of the present invention;

[0027] Figure 2 This is a schematic diagram of the structure of the first silencer of the compressor according to the first embodiment of the present invention;

[0028] Figure 3 This is an exploded view of the compressor according to the second embodiment of the present invention;

[0029] Figure 4 This is a schematic diagram of the internal structure of the compressor according to the second embodiment of the present invention;

[0030] Figure 5 Figure 4 A magnified view of part A in the middle;

[0031] Figure 6 This is a schematic diagram of the structure of the first silencer of the compressor according to the second embodiment of the present invention;

[0032] Figure 7 This is a schematic diagram of the structure of the second silencer of the compressor according to the second embodiment of the present invention;

[0033] Figure 8 This is a schematic diagram showing the change in discharge pressure between the compressor of the second embodiment of the present invention and the compressor of the comparative example;

[0034] Figure 9 The diagram shows the refrigerant flow lines of the compressor in the second embodiment of the present invention and the compressor in the comparative example.

[0035] Icon labels:

[0036] Crankcase 100, first high-pressure chamber 110, first silencing space 111, second silencing space 112, first flow hole 120, second high-pressure chamber 130, third silencing space 131, fourth silencing space 132, second flow hole 140, first boss 150, second boss 160, first silencing component 200, first air inlet 201, air outlet 202, first cylinder 210, first flange 220, first sealing cover 300, first through hole 310, second silencing component 400, second air inlet 401, second cylinder 410, second flange 420, second sealing cover 500, second through hole 510, first exhaust pipe 610, second exhaust pipe 620, first fastener 710, second fastener 720, first gasket 810, second gasket 820, third gasket 830, fourth gasket 840. Detailed Implementation

[0037] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0038] In the description of this invention, it should be understood that the orientation descriptions, such as up, down, etc., are based on the orientation or positional relationship shown in the drawings and are only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0039] In the description of this invention, "multiple" refers to two or more. The use of "first" and "second" is for distinguishing technical features only and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features or their sequential relationship.

[0040] In the description of this invention, unless otherwise explicitly defined, terms such as "set up," "install," and "connect" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this invention in conjunction with the specific content of the technical solution.

[0041] In related technologies, noise is generally categorized into aerodynamic noise, mechanical noise, and electromagnetic noise. Among aerodynamic noise, vibration noise generated during compressor exhaust accounts for a significant portion. Therefore, reducing the vibration generated during exhaust can effectively reduce exhaust noise. Existing compressors still produce substantial exhaust pulsations during operation, resulting in considerable noise from the refrigeration equipment.

[0042] Reference Figure 1 , Figure 2 , Figure 1 An exploded view of the compressor according to the first embodiment of the present invention is shown. Figure 2 A schematic diagram of the structure of the first silencer 200 of the compressor according to a first embodiment of the present invention is shown. The first embodiment of the present invention provides a compressor, which is a reciprocating compressor, for example... Figure 1 , Figure 2As shown, the compressor includes a housing, a crankcase 100, a first silencer 200, and a first sealing cover 300. The crankcase 100 is installed inside the housing and has a cylinder cavity, a first high-pressure cavity 110, and a first flow-through hole 120. The cylinder cavity and the first high-pressure cavity 110 are separated. The first sealing cover 300 covers the crankcase 100 to seal the first high-pressure cavity 110. The first silencer 200 is disposed inside the first high-pressure cavity 110. The outer peripheral wall of the first silencer 200 and the outer peripheral wall of the first high-pressure cavity 110 together define a first silencing space 111. One end of the first flow-through hole 120 is connected to the cylinder cavity, and the other end of the first flow-through hole 120 is connected to the first silencing space 111, so that the refrigerant in the cylinder cavity can flow through the cylinder cavity. The refrigerant flows into the first silencing space 111. The inner peripheral wall of the first silencing component 200, the first sealing cover 300, and the bottom wall of the first high-pressure chamber 110 enclose the second silencing space 112. The first silencing component 200 is provided with a first air inlet 201, which penetrates the first silencing component 200 so that the first silencing space 111 and the second silencing space 112 are connected. When the compressor exhausts, the refrigerant flows through the cylinder cavity, the first flow hole 120, the first silencing space 111, the first air inlet 201, and the second silencing space 112. The refrigerant is silenced in the first silencing space 111 and the second silencing space 112 respectively, which can perform two-stage silencing of the refrigerant to reduce exhaust pulsation and vibration noise.

[0043] It should be noted that the effective flow area of ​​the first flow hole 120 is smaller than the effective flow area of ​​the first silencing space 111. When the refrigerant flows into the first silencing space 111 from the first flow hole 120, on the one hand, it can buffer the refrigerant to reduce exhaust pulsation, and on the other hand, it can cause acoustic impedance mismatch, thus playing a silencing role.

[0044] Similarly, since the effective flow area of ​​the first air intake 201 is smaller than that of the second silencing space 112, when the refrigerant flows into the second silencing space 112 from the first air intake 201, it can continue to buffer the refrigerant and perform a second silencing, which can effectively reduce exhaust pulsation and vibration noise.

[0045] It is understood that at least one first silencer 200 can be configured. When there is one first silencer 200, the first high-pressure chamber 110 is divided into a first silencer space 111 and a second silencer space 112. When there are two first silencers 200, the two first silencers 200 are coaxially arranged, with one first silencer 200 located inside the other first silencer 200. The first high-pressure chamber 110 is divided into a first silencer space 111 and two second silencer spaces 112. The two first silencer spaces 111 are connected through the first air inlet 201 of the first silencer 200 located inside, which can perform three-stage silencer on the refrigerant. When there are at least three first silencers 200, at least three first silencers 200 are coaxially arranged, and adjacent second silencer spaces 112 are connected through the first air inlet 201 of the corresponding first silencer 200, which can perform multi-stage silencer on the refrigerant.

[0046] For example Figure 2 As shown, in this embodiment, the first silencer 200 includes a first cylindrical body 210 and a first flange 220. The first cylindrical body 210 is housed in the first high-pressure chamber 110 and is coaxially arranged with the first high-pressure chamber 110. The end of the first cylindrical body 210 away from the bottom wall of the first high-pressure chamber 110 is folded outward to form the first flange 220. The first flange 220 contacts the periphery of the opening of the first high-pressure chamber 110 so that the first flange 220 is sandwiched between the end wall of the first high-pressure chamber 110 facing the opening and the first sealing cover 300, which facilitates the fixing of the first flange 220 and improves the installation stability of the first silencer 200.

[0047] It should be noted that the first flange 220 is folded outward along the radial direction of the first cylinder 210 and extends in the circumferential direction. Along the axial direction of the first cylinder 210, one side of the first flange 220 abuts against the crankcase 100, and the opposite side of the first flange 220 abuts against the first sealing cover 300, which can improve the sealing effect of the first high-pressure chamber 110.

[0048] It should be noted that the first cylinder 210 and the first flange 220 are an integral structure. The first cylinder 210 and the first flange 220 can be integrally formed by stamping, which can reduce the number of molds and reduce the production cost of molds, thereby reducing the production cost of the compressor. This is not a limitation. Of course, in some other specific embodiments, the first cylinder 210 and the first flange 220 can also be connected by welding, wherein the welding method includes, but is not limited to, resistance welding, laser welding or ultrasonic welding.

[0049] It should be noted that, along the direction perpendicular to the axis of the first high-pressure chamber 110, the cross-section of the first high-pressure chamber 110 is circular, that is, the sidewall of the first high-pressure chamber 110 is arc-shaped, which can guide the refrigerant in the first silencing space 111, so that the refrigerant flow in the first silencing space 111 is more regular and more uniform, which is beneficial to reducing exhaust pulsation.

[0050] It is understandable that the outer peripheral wall of the first cylinder 210 is an arc-shaped surface. When the refrigerant ejected from the first flow hole 120 collides with the outer peripheral wall of the first cylinder 210, the outer peripheral wall of the first cylinder 210 can guide the refrigerant to move along the circumference of the first cylinder 210, so that the flow of the refrigerant is more regular and more uniform.

[0051] For example Figure 1 As shown, in this embodiment, in order to improve the sealing effect of the first high-pressure chamber 110, a first gasket 810 is provided between the first flange 220 and the first sealing cover 300. When the first silencer 200 is installed, the first cylinder 210 passes through the first gasket 810, and the first gasket 810 is sandwiched between the first flange 220 and the first sealing cover 300.

[0052] In another embodiment, a second gasket 820 is provided between the first flange 220 and the end wall of the first high-pressure chamber 110 facing the opening. When the first silencer 200 is installed, the first cylinder 210 passes through the second gasket 820, and the second gasket 820 is sandwiched between the first flange 220 and the end wall of the first high-pressure chamber 110 facing the opening. Alternatively, this can be left unrestricted.

[0053] In another embodiment, a first gasket 810 is provided between the first flange 220 and the first sealing cover 300, and a second gasket 820 is provided between the first flange 220 and the end wall of the first high-pressure chamber 110 facing the opening. Both the first gasket 810 and the second gasket 820 are annular structures. When the first silencer 200 is installed, the first cylinder 210 passes through the first gasket 810 and the second gasket 820, and the first flange 220 is sandwiched between the first gasket 810 and the second gasket 820. This is not limited here.

[0054] In this embodiment, the minimum wall thickness of the first cylinder 210 is T1, which satisfies: 1mm≤T1≤3mm. On the one hand, this ensures the structural strength of the first cylinder 210, and on the other hand, it avoids the first cylinder 210 occupying too much space in the first high-pressure chamber 110, so as to ensure that the first high-pressure chamber 110 has good noise reduction performance.

[0055] It should be noted that if T1 is less than 1mm, the minimum thickness of the first cylinder 210 is too small, the structural strength of the first cylinder 210 is reduced, and when the compressor discharges, the first high-pressure chamber 110 is in a high-pressure environment, the first cylinder 210 is prone to collapse or bend, resulting in a reduced service life of the first cylinder 210 and making it unsuitable for long-term use in high-pressure environments; the space inside the first high-pressure chamber 110 is limited. If T1 is greater than 3mm, the minimum thickness of the first cylinder 210 is too large, the effective usable space inside the first high-pressure chamber 110 is reduced, resulting in poor noise reduction effect of the compressor.

[0056] It should be noted that the value of T1 can be 1mm, 1.2mm, 1.4mm, 1.6mm, 1.8mm, 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, or 3mm, and there are no restrictions here.

[0057] In this embodiment, along the axial direction of the first cylinder 210, the minimum thickness of the first flange 220 is T2, which satisfies: 1mm≤T2≤2mm. On the one hand, this ensures the structural strength of the first flange 220, and on the other hand, it reduces the overall height of the compressor.

[0058] It should be noted that if T2 is less than 1mm, the minimum thickness of the first flange 220 is too small, the structural strength of the first flange 220 is reduced, and when the compressor discharges, the first high-pressure chamber 110 is in a high-pressure environment. Cracks are easily generated at the connection between the first cylinder 210 and the first flange 220, which leads to a reduction in the service life of the first silencer 200. If T2 is greater than 2mm, the minimum thickness of the first flange 220 is too large, the effective space in the first high-pressure chamber 110 is reduced, resulting in poor noise reduction effect of the compressor.

[0059] It should be noted that the value of T2 can be 1mm, 1.2mm, 1.4mm, 1.6mm, 1.8mm, or 2mm, and there are no restrictions here.

[0060] In this embodiment, the bottom wall of the first high-pressure chamber 110 is provided with a first boss 150, the first cylinder 210 is sleeved on the outer periphery of the first boss 150, and the first sealing cover 300 is connected to the first boss 150 by a first fastener 710, which is a bolt or screw, etc., so that the first sealing cover 300 and the crankcase 100 can be stably connected, and its installation is more convenient.

[0061] It should be noted that when assembling the first silencer 200, the end of the first cylinder 210 furthest from the first sealing cover 300 is sealed against the bottom wall of the first high-pressure chamber 110. This prevents the refrigerant in the first silencer space 111 from entering the second silencer space 112 through the gap between the first cylinder 210 and the bottom wall of the first high-pressure chamber 110, thus making the flow of the refrigerant in the first high-pressure chamber 110 more regular and uniform. As another embodiment, a sealing gasket can also be provided between the first cylinder 210 and the bottom wall of the first high-pressure chamber 110, which can also prevent the refrigerant in the first silencer space 111 from entering the second silencer space 112 through the gap between the first cylinder 210 and the bottom wall of the first high-pressure chamber 110. This is not a limitation.

[0062] In this embodiment, along the radial direction of the first cylinder 210, the maximum width of the first boss 150 is less than the minimum inner diameter of the first silencer 200. On the one hand, this can avoid interference between the first boss 150 and the first silencer 200, so as to facilitate the assembly of the first silencer 200. On the other hand, it can ensure that the second silencer space 112 has a sufficiently large space to effectively buffer the refrigerant entering the second silencer space 112.

[0063] It should be noted that, for example, Figure 2 As shown, the minimum inner diameter of the first muffler 200 is D1, satisfying 7mm≤D1≤10mm. This avoids interference between the first boss 150 and the first muffler 200 while ensuring that the second muffler space 112 has a sufficiently large space. If D1 is less than 7mm, to avoid interference between the first boss 150 and the first muffler 200, the maximum width of the first boss 150 must also be less than 7mm. However, since the first boss 150 is threaded to the first fastener 710, if the maximum width of the first boss 150 is less than 7mm, the structural strength of the first boss 150 is reduced, which is not conducive to fixing the first sealing cover 300. If D1 is greater than 10mm, the minimum inner diameter of the first muffler 200 is too large, the space inside the first high-pressure chamber 110 is limited, and the volume of the first muffler space 111 is too small, which is not conducive to buffering the refrigerant.

[0064] It should be noted that the value of D1 can be 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm and 10mm, and there is no restriction here.

[0065] In this embodiment, the compressor also includes a first exhaust pipe 610, which passes through the first sealing cover 300 and one end of the first exhaust pipe 610 extends into the second silencing space 112. This ensures that the refrigerant in the first high-pressure chamber 110 can only be discharged after entering the second silencing space 112, thus preventing the situation where some refrigerant is discharged without entering the second silencing space 112. This reduces exhaust pulsation and exhaust noise.

[0066] It should be noted that in this embodiment, the first sealing cover 300 is provided with a first through hole 310, and one end of the first exhaust pipe 610 is housed in the second silencing space 112 through the first through hole 310, which facilitates the installation of the first exhaust pipe 610.

[0067] Reference Figures 3 to 7 , Figure 3 This is an exploded view of the compressor according to the second embodiment of the present invention. Figure 4 This is a schematic diagram of the internal structure of the compressor according to the second embodiment of the present invention. Figure 5 for Figure 4 A magnified view of part A in the middle. Figure 6 This is a schematic diagram of the structure of the first silencer 200 of the compressor according to the second embodiment of the present invention. Figure 7 This is a schematic diagram of the structure of the second silencer 400 of the compressor according to the second embodiment of the present invention. For example... Figures 3 to 7 As shown, based on the first embodiment, the second embodiment of the present invention proposes a compressor, which further includes a second silencer 400 and a second sealing cover 500. The crankcase 100 has a second high-pressure chamber 130 and a second flow passage 140. The cylinder chamber, the first high-pressure chamber 110, and the second high-pressure chamber 130 are separated from each other. The first silencer 200 is provided with an exhaust port 202, which penetrates the first silencer 200. The second silencer 400 is housed in the second high-pressure chamber 130. The outer peripheral wall of the second silencer 400 and the inner peripheral wall of the second high-pressure chamber 130 together define a third silencer space 131. One end of the second flow passage 140 is connected to the first silencer space 111, and the other end of the second flow passage 140 is connected to the third silencer space 131. The inner peripheral wall of the second silencer 400, the second sealing cover 500, and the second high-pressure chamber 130 are separated from each other. The bottom walls of the two high-pressure chambers 130 enclose a fourth silencing space 132. The second silencing component 400 is provided with a second air inlet 401, which penetrates the second silencing component 400 to connect the third silencing space 131 and the fourth silencing space 132. Thus, when the compressor exhausts, the refrigerant flows in the following direction: cylinder chamber - first flow hole 120 - first silencing space 111 - first air inlet 201 - second silencing space 112 - air outlet 202 - first silencing space 111 - second flow hole 140 - third silencing space 131 - second air inlet 401 - fourth silencing space 132. The refrigerant is silenced in the first silencing space 111, the second silencing space 112, the third silencing space 131, and the fourth silencing space 132, which can perform multiple silencing operations to reduce exhaust pulsation and vibration noise.

[0068] It should be noted that the compressor may also include a third silencer and a third sealing cover. The crankcase 100 has a corresponding third high-pressure chamber and a third flow hole. The second high-pressure chamber 130 is connected to the third high-pressure chamber through the third flow hole. The third silencer is located in the third high-pressure chamber to divide the third high-pressure chamber into a fifth silencer space and a sixth silencer space. The third silencer is provided with a third air inlet. The fifth silencer space is connected to the sixth silencer space through the third air inlet. The third sealing cover is used to seal the third high-pressure chamber, which can perform multi-stage silencer on the refrigerant to reduce exhaust pulsation and vibration noise.

[0069] It is understood that at least one second silencer 400 can be configured. When there is one second silencer 400, the second high-pressure chamber 130 is divided into a third silencer space 131 and a fourth silencer space 132. When there are two second silencers 400, the two second silencers 400 are coaxially arranged, with one second silencer 400 located inside the other second silencer 400. The second high-pressure chamber 130 is divided into a third silencer space 131 and two fourth silencer spaces 132. The two fourth silencer spaces 132 are connected through the second air inlet 401 of the second silencer 400 located inside, which can perform multi-stage silencing of the refrigerant. When there are at least three second silencers 400, the at least three second silencers 400 are coaxially arranged, and adjacent fourth silencer spaces 132 are connected through the second air inlet 401 of the corresponding second silencer 400, which can perform multi-stage silencing of the refrigerant.

[0070] For example Figure 4 As shown, in this embodiment, in order to make the refrigerant flow more uniform in the first high-pressure chamber 110, the first air inlet 201 is set on the side of the first silencer 200 near the first flow-through hole 120, and the first air inlet 201 is arranged opposite to the first flow-through hole 120, so that more refrigerant can enter the second silencer space 112, which can reduce the amount of refrigerant that directly enters the third silencer space 131 from the first silencer space 111, thereby reducing the refrigerant flow rate.

[0071] It should be noted that when the compressor discharges, the refrigerant in the cylinder cavity flows into the first silencing space 111 through the first flow-through hole 120. Since the first air inlet 201 is positioned opposite to the first flow-through hole 120, some of the refrigerant in the first silencing space 111 can quickly flow into the second silencing space 112, which can divert the refrigerant to reduce the refrigerant flow rate, making the refrigerant flow more regular and ensuring that the refrigerant flow in the first high-pressure chamber 110 is more uniform.

[0072] It is understandable that if the first air inlet 201 is located on the side of the first silencer 200 away from the first flow hole 120, most of the refrigerant in the first silencer space 111 will flow directly into the third silencer space 131, while too little refrigerant will enter the second silencer space 112 from the first silencer space 111, which will not effectively reduce the flow rate of the refrigerant.

[0073] For example Figure 5 As shown, in this embodiment, the first air inlet 201 and the air outlet 202 are staggered along the circumference of the first silencing component 200, which can prevent the refrigerant flowing into the second silencing space 112 from the first air inlet 201 from colliding with the refrigerant flowing out of the second silencing space 112 from the air outlet 202, so that the flow of the refrigerant is more regular and more uniform.

[0074] It should be noted that the refrigerant flowing out of the second silencing space 112 from the air outlet 202 can collide with the side wall of the first high-pressure chamber 110, which can reduce the flow rate of the refrigerant and help reduce exhaust pulsation.

[0075] It should be noted that the minimum angle between the line connecting the center of the first air inlet 201 and the center of the first muffler 200 and the line connecting the center of the air outlet 202 and the center of the first muffler 200 is θ, which satisfies: 30°≤θ≤180°. The value of θ can be 30°, 40°, 50°, 60°, 70°, 80°, 90°, 100°, 110°, 120°, 130°, 140°, 150°, 160°, 170° and 180°. This can prevent the refrigerant flowing into the second muffler space 112 from the first air inlet 201 from colliding with the refrigerant flowing out of the second muffler space 112 from the air outlet 202, so that the flow of the refrigerant is more regular and more uniform.

[0076] For example Figure 3 As shown, in this embodiment, the compressor also includes a second exhaust pipe 620. The second exhaust pipe 620 passes through the second sealing cover 500 and one end of the second exhaust pipe 620 extends into the fourth silencing space 132, so that the refrigerant in the second high-pressure chamber 130 can only be discharged after entering the fourth silencing space 132. This can prevent the situation where some refrigerant is discharged without entering the fourth silencing space 132, reduce exhaust pulsation, and reduce exhaust noise.

[0077] It should be noted that in this embodiment, the second sealing cover 500 is provided with a second through hole 510, and one end of the second exhaust pipe 620 is housed in the fourth silencing space 132 through the second through hole 510, which facilitates the installation of the second exhaust pipe 620.

[0078] It should be noted that in this embodiment, there is no need to provide a first exhaust pipe 610 on the first sealing cover 300.

[0079] In this embodiment, the specific structure of the first silencer 200 is similar to that of the first silencer 200 of the compressor in the first embodiment of the present invention, and will not be described again here.

[0080] For example Figure 6 As shown, in this embodiment, the second silencer 400 includes a second cylindrical body 410 and a second flange 420. The second cylindrical body 410 is housed within the second high-pressure chamber 130 and is coaxially arranged with the second high-pressure chamber 130. The end of the second cylindrical body 410 away from the bottom wall of the second high-pressure chamber 130 is folded outward to form the second flange 420. The second flange 420 contacts the periphery of the opening of the second high-pressure chamber 130, so that the second flange 420 is sandwiched between the end wall of the second high-pressure chamber 130 facing the opening and the second sealing cover 500, which facilitates the fixing of the second flange 420 and improves the installation stability of the second silencer 400.

[0081] It should be noted that the second flange 420 is folded outward along the radial direction of the second cylinder 410 and extends in the circumferential direction. Along the axial direction of the second cylinder 410, one side of the second flange 420 abuts against the crankcase 100, and the opposite side of the second flange 420 abuts against the second sealing cover 500, which can improve the sealing effect of the second high-pressure chamber 130.

[0082] It should be noted that, for example, Figure 5 As shown, in order to improve the sealing effect of the second high-pressure chamber 130, a third gasket 830 is provided between the second flange 420 and the second sealing cover 500, and a fourth gasket 840 is provided between the second flange 420 and the end wall of the second high-pressure chamber 130 facing the opening. When the second silencer 400 is installed, the second flange 420 is sandwiched between the third gasket 830 and the fourth gasket 840.

[0083] It is understood that the second cylinder 410 and the second flange 420 are an integral structure. The second cylinder 410 and the second flange 420 can be integrally formed by stamping, which can reduce the number of molds and reduce the production cost of the molds, thereby reducing the production cost of the compressor. This is not a limitation. Of course, in some other specific embodiments, the second cylinder 410 and the second flange 420 can also be connected by welding, wherein the welding method includes, but is not limited to, resistance welding, laser welding or ultrasonic welding.

[0084] In this embodiment, the minimum thickness of the second cylinder 410 along the radial direction is T3, which satisfies: 1mm≤T3≤3mm. On the one hand, this ensures the structural strength of the second cylinder 410, and on the other hand, it avoids the second cylinder 410 occupying too much space in the second high-pressure chamber 130, so as to ensure that the second high-pressure chamber 130 has good noise reduction performance.

[0085] It should be noted that if T3 is less than 1mm, the minimum thickness of the second cylinder 410 is too small, the structural strength of the second cylinder 410 is reduced, and when the compressor discharges, the second high-pressure chamber 130 is in a high-pressure environment, the second cylinder 410 is prone to collapse or bend, resulting in a reduced service life of the second cylinder 410 and making it unsuitable for long-term use in high-pressure environments; the space inside the second high-pressure chamber 130 is limited. If T3 is greater than 3mm, the minimum thickness of the second cylinder 410 is too large, the effective usable space inside the second high-pressure chamber 130 is reduced, resulting in poor noise reduction effect of the compressor.

[0086] It should be noted that the value of T3 can be 1mm, 1.2mm, 1.4mm, 1.6mm, 1.8mm, 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, or 3mm, and there are no restrictions here.

[0087] In this embodiment, along the axial direction of the second cylinder 410, the minimum thickness of the second flange 420 is T4, which satisfies: 1mm≤T4≤2mm. On the one hand, this ensures the structural strength of the second flange 420, and on the other hand, it reduces the overall height of the compressor.

[0088] It should be noted that if T4 is less than 1mm, the minimum thickness of the second flange 420 is too small, the structural strength of the second flange 420 is reduced, and the second high-pressure chamber 130 is in a high-pressure environment when the compressor is discharging. Cracks are likely to occur at the connection between the second cylinder 410 and the second flange 420, which will reduce the service life of the second muffler 400. If T4 is greater than 2mm, the minimum thickness of the second flange 420 is too large, the effective space in the second high-pressure chamber 130 is reduced, and the muffler effect of the compressor is poor.

[0089] For example Figure 4 As shown, in this embodiment, the bottom wall of the second high-pressure chamber 130 is provided with a second boss 160, the second cylinder 410 is sleeved on the second boss 160, and the second sealing cover 500 is connected to the second boss 160 by a second fastener 720. The second fastener 720 is a bolt or screw or other component, so that the second sealing cover 500 and the crankcase 100 can achieve a stable connection, and its installation is more convenient.

[0090] In this embodiment, along the radial direction of the second cylinder 410, the maximum width of the second boss 160 is less than the minimum inner diameter of the second silencer 400. On the one hand, this can avoid interference between the second boss 160 and the second silencer 400, so as to facilitate the assembly of the second silencer 400. On the other hand, it can ensure that the fourth silencer space 132 has a sufficiently large space to effectively buffer the refrigerant entering the fourth silencer space 132.

[0091] It should be noted that, for example, Figure 7 As shown, the minimum inner diameter of the second muffler 400 is D2, which satisfies the condition: 7mm ≤ D2 ≤ 10mm. This avoids interference between the second boss 160 and the second muffler 400 while ensuring that the fourth muffler space 132 has a sufficiently large space. If D2 is less than 7mm, to avoid interference between the second boss 160 and the second muffler 400, the maximum width of the second boss 160 must also be less than 7mm. However, since the second boss 150 is threaded to the second fastener 720, if the maximum width of the second boss 160 is less than 7mm, the structural strength of the second boss 160 will be reduced, which is not conducive to fixing the second sealing cover 500. If D2 is greater than 10mm, the minimum inner diameter of the second muffler 400 will be too large, the space inside the second high-pressure chamber 130 will be limited, and the volume of the third muffler space 131 will be too small, which is not conducive to buffering the refrigerant.

[0092] It should be noted that the value of D2 can be 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm and 10mm, and there is no restriction here.

[0093] Reference Figure 8 , Figure 9 , Figure 8 This is a schematic diagram showing the change in exhaust pressure in the second embodiment and the comparative example of the present invention. Figure 9 This is a streamline diagram of the refrigerant in the second embodiment and the comparative example of the present invention. In the comparative example, the compressor does not include the first silencer 200 and the second silencer 400. The refrigerant in the first high-pressure chamber 110 directly enters the second high-pressure chamber 130 through the second flow-through hole 140. The remaining components of the compressor in the comparative example are the same as those of the compressor in the second embodiment of the present invention.

[0094] Depend on Figure 8 It can be seen that by comparing the discharge pressure of the compressor in the second embodiment with that of the comparative compressor, it is found that the discharge pressure of the compressor in the second embodiment is significantly improved at the trough, the trough stabilization speed is faster and the pressure is higher at this point. After processing the data of the three cycles, the standard deviation is obtained and compared. The standard deviation of the discharge pressure of the comparative compressor is 305.15 Pa, while the standard deviation of the discharge pressure of the compressor in the second embodiment is 290.96 Pa, and the overall discharge pressure is reduced by about 5%.

[0095] Depend on Figure 9It can be seen that the refrigerant flow in the comparative compressor is very turbulent, with a maximum flow velocity of 53.95 m / s. In addition, a darker-colored area appears in the second high-pressure chamber 130 of the comparative compressor, where the refrigerant concentrates its flow. In contrast, the refrigerant flow in the compressor of the second embodiment is significantly more regular. No darker-colored area appears in the second high-pressure chamber 130 of the compressor of the second embodiment, and the refrigerant flow in the second flow hole 140 is more uniform, with a maximum flow velocity of only 44.59 m / s. Therefore, by setting the first silencer 200 and the second silencer 400, it is beneficial to reduce exhaust pulsation.

[0096] The refrigeration device of the third embodiment of the present invention includes the compressor of the above embodiments. The refrigeration device can be a refrigerator, freezer, etc.

[0097] Since the refrigeration equipment adopts all the technical solutions of the compressor in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments, which will not be repeated here.

[0098] The present invention has been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiment. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention.

Claims

1. A compressor, characterized in that, include: case; A crankcase, installed within the housing, the crankcase having a cylinder chamber, a first high-pressure chamber, and a first flow passage, the first flow passage being configured to connect the cylinder chamber and the first high-pressure chamber; The first sealing cap is placed over the opening of the first high-pressure chamber; A first silencing component is disposed within the first high-pressure chamber. The outer peripheral wall of the first silencing component and the inner peripheral wall of the first high-pressure chamber together define a first silencing space. The lower end of the peripheral wall of the first silencing component abuts against the bottom wall of the first high-pressure chamber, and the upper end of the peripheral wall of the first silencing component abuts against the first sealing cover. The inner peripheral wall of the first silencing component, the first sealing cover, and the bottom wall of the first high-pressure chamber enclose a second silencing space. The first silencing component is provided with a first air inlet, and the first silencing space is connected to the second silencing space through the first air inlet. The crankcase has a second high-pressure chamber and a second flow passage. A second silencer is provided in the second high-pressure chamber. The crankcase has a second sealing cover, which seals the opening of the second high-pressure chamber. The first silencer has an exhaust port that penetrates its peripheral wall. The inner peripheral wall of the second high-pressure chamber and the outer peripheral wall of the second silencer together define a third silencer space. The second flow passage is configured to connect the first silencer space and the third silencer space. The lower end of the peripheral wall of the first silencer abuts against the bottom wall of the second high-pressure chamber, and the upper end of the peripheral wall of the first silencer abuts against the second sealing cover. The inner peripheral wall of the second silencer, the second sealing cover, and the bottom wall of the second high-pressure chamber enclose a fourth silencer space. The second silencer has a second air inlet. The third silencer space is connected to the fourth silencer space through the second air inlet. The first air inlet is located on the side of the first silencer close to the first flow passage, and the first air inlet is opposite to the first flow passage. The first air inlet and the exhaust port are offset along the circumference of the first silencer.

2. The compressor according to claim 1, characterized in that: The first silencer includes a first cylinder and a first flange. The first air inlet is located on the first cylinder along the axial direction of the first cylinder. The first flange is located at one end of the first cylinder near the first sealing cover. The first flange is arranged around the outer peripheral wall of the first cylinder and is sandwiched between the end wall of the first high-pressure chamber facing the opening and the first sealing cover.

3. The compressor according to claim 2, characterized in that: A first gasket is provided between the first flange and the first sealing cover, and / or a second gasket is provided between the end wall of the first high-pressure chamber facing the opening and the first flange.

4. The compressor according to claim 2, characterized in that: The minimum wall thickness of the first cylinder is T1, which satisfies: 1mm≤T1≤3mm.

5. The compressor according to claim 2, characterized in that: Along the axial direction of the first cylinder, the minimum thickness of the first flange is T2, which satisfies: 1mm≤T2≤2mm.

6. The compressor according to claim 2, characterized in that: The bottom wall of the first high-pressure chamber is provided with a first protrusion, the first sealing cover is connected to the first protrusion by a first fastener, the first cylinder is sleeved on the outer periphery of the first protrusion, and the lower end of the first cylinder is sealed and abutted against the bottom wall of the first high-pressure chamber.

7. The compressor according to claim 2, characterized in that: The minimum inner diameter of the first muffler is D1, which satisfies the following condition: 7mm≤D1≤10mm.

8. The compressor according to claim 1, characterized in that: The compressor also includes a first exhaust pipe, one end of which passes through the first sealing cover and extends into the second silencing space.

9. The compressor according to claim 1, characterized in that: The compressor also includes a second exhaust pipe, one end of which passes through the second sealing cover and extends into the fourth silencing space.

10. A refrigeration device, characterized in that: Includes the compressor described in any one of claims 1-9.

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