Compressor and refrigeration equipment

Abstract

The compressor comprises a shell, a crankcase, a first silencing part and a first sealing cover, the crankcase is installed in the shell and provided with a cylinder cavity, a first high-pressure cavity and a first overflowing hole, and the first overflowing hole is configured to communicate with the cylinder cavity and the first high-pressure cavity; the first sealing cover covers an opening of the first high-pressure cavity in a sealing mode, the first silencing part is arranged in the first high-pressure cavity, a first silencing space is jointly defined by the outer circumferential wall of the first silencing part and the inner circumferential wall of the first high-pressure cavity, and a second silencing space is defined by the inner circumferential wall of the first silencing part, the first sealing cover and the bottom wall of the first high-pressure cavity; and the first silencing part is provided with a first air inlet hole, the first silencing space communicates with the second silencing space through the first air inlet hole, when the compressor exhausts air, the refrigerant is subjected to silencing in the first silencing space and the second silencing space, secondary silencing can be conducted on the refrigerant, and therefore exhaust pulsation and vibration noise are reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a compressor and a refrigeration device. Background Art

[0002] With the continuous development of society, people's living standards are gradually improving, and the noise requirements for refrigerators are getting higher and higher. As the main source of refrigerator noise, compressors also have higher requirements for their noise performance. Generally speaking, noise is divided into pneumatic noise, mechanical noise and electromagnetic noise. Among pneumatic noise, the vibration noise generated by the compressor during exhaust accounts for a large proportion. Therefore, reducing the vibration generated during exhaust can effectively reduce exhaust noise. Existing compressors still produce large exhaust pulsations when working, which causes the refrigeration equipment to produce large noise. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a compressor that can reduce exhaust pulsation to reduce vibration noise.

[0004] The present invention also provides a refrigeration device having the compressor.

[0005] A compressor according to a first embodiment of the present invention comprises:

[0006] case;

[0007] A crankcase, installed in the housing, the crankcase having a cylinder cavity, a first high-pressure cavity and a first flow hole, wherein the first flow hole is configured to connect the cylinder cavity and the first high-pressure cavity;

[0008] A first sealing cover, sealing the opening of the first high-pressure chamber;

[0009] A first silencer is arranged in the first high-pressure chamber, and the outer peripheral wall of the first silencer and the inner peripheral wall of the first high-pressure chamber jointly define a first silencer space, the lower end of the peripheral wall of the first silencer abuts against the bottom wall of the first high-pressure chamber, and the upper end of the peripheral wall of the first silencer abuts against the first sealing cover, the inner peripheral wall of the first silencer, the first sealing cover and the bottom wall of the first high-pressure chamber together form a second silencer space, and the first silencer is provided with a first air inlet hole, and the first silencer space is connected to the second silencer space through the first air inlet hole.

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

[0011] When the compressor is exhausting, the flow direction of the refrigerant is the cylinder cavity, the first flow hole, the first silencer space, the first air inlet hole and the second silencer space. The refrigerant is silenced in the first silencer space and the second silencer space respectively. The refrigerant can be silenced at two levels 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 provided in the first cylinder, along the axial direction of the first cylinder, the first flange is provided at one end of the first cylinder close to the first sealing cover, the first flange is arranged around the outer peripheral wall of the first cylinder, and the first flange is clamped 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 boss, the first sealing cover is connected to the first boss via a first fastener, the first cylinder is sleeved on the outer periphery of the first boss, and the lower end of the first cylinder is sealingly abutted against 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 silencer is D1, which satisfies: 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 muffler space.

[0019] According to some embodiments of the present invention, the crankcase has a second high-pressure chamber and a second flow hole, a second muffler is provided in the second high-pressure chamber, the crankcase is provided with a second sealing cover, the second sealing cover is sealed at the opening of the second high-pressure chamber, the first muffler is provided with an air outlet hole running through its peripheral wall, the inner peripheral wall of the second high-pressure chamber and the outer peripheral wall of the second muffler jointly define a third muffler space, the second flow hole is configured to connect the first muffler space and the third muffler space, the lower end of the peripheral wall of the first muffler abuts the bottom wall of the second high-pressure chamber, the upper end of the peripheral wall of the first muffler abuts the second sealing cover, the inner peripheral wall of the second muffler, the second sealing cover and the bottom wall of the second high-pressure chamber enclose a fourth muffler space, the second muffler is provided with a second air inlet hole, and the third muffler space is connected to the fourth muffler space through the second air inlet hole.

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

[0021] According to some embodiments of the present invention, the first air inlet and the air outlet are staggered along the circumferential direction 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 is inserted into the second sealing cover, and one end of which extends into the fourth silencing space.

[0023] A refrigeration device according to a third embodiment of the present invention comprises the compressor described in the above embodiment.

[0024] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0026] Figure 1 It is an exploded schematic diagram of a compressor according to a first embodiment of the present invention;

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

[0028] Figure 3 is an exploded schematic diagram of a compressor according to a second embodiment of the present invention;

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

[0030] Figure 5 Figure 4 A partial enlarged view of part A;

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

[0032] Figure 7 A schematic structural diagram of a second silencer of a compressor according to a second embodiment of the present invention;

[0033] Figure 8 A schematic diagram of changes in exhaust pressure of a compressor according to a second embodiment of the present invention and a compressor according to a comparative example;

[0034] Fig. 9 Flow diagram of the refrigerant of the compressor according to the second embodiment of the present invention and the compressor according to the comparative example.

[0035] Figure Number:

[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 muffler 200, first air inlet 201, air outlet 202, first cylinder 210, first flange 220, first sealing cover 300, first through hole 310, second muffler 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 DESCRIPTION

[0037] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

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

[0039] In the description of the present invention, "a plurality" means more than two. If there is a description of "first" or "second", it is only used for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0040] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0041] In the related art, generally speaking, noise is divided into pneumatic noise, mechanical noise and electromagnetic noise. Among pneumatic noise, the vibration noise generated when the compressor is exhausted accounts for a large proportion. Therefore, reducing the vibration generated during exhaust can effectively reduce the exhaust noise. Existing compressors still generate large exhaust pulsations when working, which causes the refrigeration equipment to generate large noise.

[0042] Reference Figure 1 , Figure 2 , Figure 1 FIG. 2 shows an exploded schematic diagram of a compressor according to a first embodiment of the present invention. Figure 2 The first embodiment of the present invention provides a compressor, which is a reciprocating compressor, such as Figure 1 , Figure 2As shown, the compressor includes a shell, a crankcase 100, a first muffler 200 and a first sealing cover 300. The crankcase 100 is installed inside the shell. The crankcase 100 has a cylinder cavity, a first high-pressure cavity 110 and a first flow hole 120. The cylinder cavity and the first high-pressure cavity 110 are separated. The first sealing cover 300 is covered on the crankcase 100 to seal the first high-pressure cavity 110. The first muffler 200 is arranged in the first high-pressure cavity 110. The outer peripheral wall of the first muffler 200 and the outer peripheral wall of the first high-pressure cavity 110 jointly define a first muffler space 111. One end of the first flow hole 120 is connected to the cylinder cavity, and the other end of the first flow hole 120 is connected to the first muffler space 111, so that the refrigerant in the cylinder cavity can The refrigerant flows into the first silencer space 111, and the inner wall of the first silencer 200, the first sealing cover 300 and the bottom wall of the first high-pressure chamber 110 enclose the second silencer space 112. The first silencer 200 is provided with a first air inlet hole 201, and the first air inlet hole 201 penetrates the first silencer 200 to connect the first silencer space 111 with the second silencer space 112. When the compressor is exhausted, the flow direction of the refrigerant is the cylinder cavity, the first flow hole 120, the first silencer space 111, the first air inlet hole 201 and the second silencer space 112. The refrigerant is silenced in the first silencer space 111 and the second silencer space 112 respectively, and the refrigerant can be silenced at two levels to reduce exhaust pulsation and vibration noise.

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

[0044] Similarly, the effective flow area of ​​the first air inlet 201 is smaller than the effective flow area of ​​the second silencing space 112. When the refrigerant flows from the first air inlet 201 into the second silencing space 112, the refrigerant can continue to be buffered to perform a second silencing on the refrigerant, which can effectively reduce exhaust pulsation and vibration noise.

[0045] It can be understood that at least one first silencer 200 can be configured. When one first silencer 200 is configured, the first high-pressure chamber 110 is divided into a first silencer space 111 and a second silencer space 112; when two first silencers 200 are configured, the two first silencers 200 are coaxially arranged, one of the first silencers 200 is located on the inner side of the other first silencer 200, and the first high-pressure chamber 110 is divided into a first silencer space 111 and two second silencer spaces 112, and the two first silencer spaces 111 are connected through the first air inlet 201 of the first silencer 200 located on the inner side, so that the refrigerant can be silenced in three stages; when at least three first silencers 200 are configured, 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, so that the refrigerant can be silenced in multiple stages.

[0046] For example Figure 2 As shown, in this embodiment, the first silencer 200 includes a first cylinder 210 and a first flange 220. The first cylinder 210 is accommodated in the first high-pressure chamber 110, and the first cylinder 210 is coaxially arranged with the first high-pressure chamber 110. One end of the first cylinder 210 away from the bottom wall of the first high-pressure chamber 110 is folded outward to form a 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 clamped between the end wall of the first high-pressure chamber 110 facing the opening and the first sealing cover 300, which can facilitate the fixing of the first flange 220 to improve the installation stability of the first silencer 200.

[0047] It should be noted that along the radial direction of the first cylinder 210, the first flange 220 is folded outward, and the first flange 220 is extended 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 other 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 integrated structure, and the first cylinder 210 and the first flange 220 can be integrally formed by stamping, which can reduce the number of molds, thereby reducing the production and manufacturing costs of the molds, thereby reducing the production and manufacturing costs of the compressor, which is not limited here. Of course, in 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 axial direction of the first high-pressure chamber 110, the cross-section of the first high-pressure chamber 110 is a circular structure, that is, the side wall of the first high-pressure chamber 110 is arc-shaped, which can drain the refrigerant in the first silencer space 111, so that the refrigerant flow in the first silencer space 111 is more regular and more uniform, which is beneficial to reduce exhaust pulsation.

[0050] It can be understood that the outer peripheral wall of the first cylinder 210 corresponds to an arc-shaped surface. When the refrigerant sprayed 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 to make the flow of the refrigerant 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 arranged between the first flange 220 and the first sealing cover 300. When the first silencer 200 is installed, the first cylinder 210 is passed through the first gasket 810, and the first gasket 810 is clamped between the first flange 220 and the first sealing cover 300.

[0052] As 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 is passed through the second gasket 820, and the second gasket 820 is clamped between the first flange 220 and the end wall of the first high-pressure chamber 110 facing the opening. No limitation is made here.

[0053] As another embodiment, a first gasket 810 is arranged between the first flange 220 and the first sealing cover 300, and a second gasket 820 is arranged between the first flange 220 and the end wall of the first high-pressure chamber 110 facing the opening. The first gasket 810 and the second gasket 820 are both annular structures. When the first silencer 200 is installed, the first cylinder 210 is passed through the first gasket 810 and the second gasket 820, and the first flange 220 is clamped between the first gasket 810 and the second gasket 820. No limitation is made 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, the structural strength of the first cylinder 210 can be ensured. On the other hand, the first cylinder 210 can be prevented from occupying too much space in the first high-pressure chamber 110, so as to ensure that the first high-pressure chamber 110 has good sound-absorbing performance.

[0055] It should be noted that if T1 is less than 1 mm, 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 is exhausted, the first high-pressure chamber 110 is a high-pressure environment. The first cylinder 210 is prone to collapse or bend, resulting in a reduction in the service life of the first cylinder 210, and it cannot be used in a high-pressure environment for a long time; the space in the first high-pressure chamber 110 is limited. If T1 is greater than 3 mm, the minimum thickness of the first cylinder 210 is too large, and the effectively utilized space in the first high-pressure chamber 110 is reduced, resulting in poor silencing effect of the compressor.

[0056] It should be pointed out 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, without limitation herein.

[0057] In this embodiment, along the axial direction of the first cylinder 210, the minimum thickness of the first flange 220 is T2, satisfying: 1mm≤T2≤2mm. On the one hand, the structural strength of the first flange 220 can be ensured, and on the other hand, the overall height of the compressor can be reduced.

[0058] It should be noted that if T2 is less than 1 mm, 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 is exhausted, the first high-pressure chamber 110 is a high-pressure environment. Cracks are easily generated at the connection position between the first cylinder 210 and the first flange 220, resulting in a reduction in the service life of the first silencer 200; if T2 is greater than 2 mm, the minimum thickness of the first flange 220 is too large, and the effectively utilized space in the first high-pressure chamber 110 is reduced, resulting in poor silencer effect of the compressor.

[0059] It should be pointed out that the value of T2 can be 1mm, 1.2mm, 1.4mm, 1.6mm, 1.8mm, or 2mm, without limitation herein.

[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 through a first fastener 710. The first fastener 710 is a bolt or a screw, etc., so that a stable connection is achieved between the first sealing cover 300 and the crankcase 100, and its installation is more convenient.

[0061] It should be noted that when the first silencer 200 is assembled, the end of the first cylinder 210 away from the first sealing cover 300 is sealed against the bottom wall of the first high-pressure chamber 110, which can prevent the refrigerant in the first silencer space 111 from entering the second silencer space 112 from the gap between the first cylinder 210 and the bottom wall of the first high-pressure chamber 110, so that the flow of the refrigerant in the first high-pressure chamber 110 is more regular and more 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 from the gap between the first cylinder 210 and the bottom wall of the first high-pressure chamber 110, which is not limited here.

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

[0063] It should be noted that, for example Figure 2 As shown, the minimum inner diameter of the first silencer 200 is D1, which satisfies: 7mm≤D1≤10mm, which can avoid the interference between the first boss 150 and the first silencer 200, and ensure that the second silencer space 112 has a large enough space. If D1 is less than 7mm, in order to avoid the interference between the first boss 150 and the first silencer 200, the maximum width of the first boss 150 must also be less than 7mm, and the first boss 150 is threadedly connected to the first fastener 710. When 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 silencer 200 is too large, the space in the first high-pressure chamber 110 is limited, and the volume of the first silencer 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, without limitation herein.

[0065] In this embodiment, the compressor also includes a first exhaust pipe 610, which is passed through the first sealing cover 300 and one end of the first exhaust pipe 610 extends into the second silencer space 112, so that the refrigerant in the first high-pressure chamber 110 can only be discharged after entering the second silencer space 112, which can avoid the situation where part of the refrigerant is discharged before entering the second silencer space 112, and can reduce 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 accommodated in the second silencing space 112 through the first through hole 310 , which can facilitate the installation of the first exhaust pipe 610 .

[0067] Reference Figures 3 to 7 , Figure 3 is an exploded schematic diagram of a compressor according to a second embodiment of the present invention, Figure 4 is a schematic diagram of the internal structure of a compressor according to a second embodiment of the present invention, Figure 5 for Figure 4 A partial enlarged view of part A. Figure 6 This is a schematic structural diagram of a first silencer 200 of a compressor according to a second embodiment of the present invention. Figure 7 FIG. 4 is a schematic structural diagram of a second silencer 400 of a compressor according to a second embodiment of the present invention. Figures 3 to 7 As shown, on the basis of the first embodiment, the second embodiment of the present invention proposes a compressor, the compressor also includes a second muffler 400 and a second sealing cover 500, the crankcase 100 has a second high-pressure chamber 130 and a second flow hole 140, the cylinder chamber, the first high-pressure chamber 110 and the second high-pressure chamber 130 are separated from each other, the first muffler 200 is provided with an air outlet 202, the air outlet 202 runs through the first muffler 200, the second muffler 400 is accommodated in the second high-pressure chamber 130, the outer peripheral wall of the second muffler 400 and the inner peripheral wall of the second high-pressure chamber 130 jointly define a third muffler space 131, one end of the second flow hole 140 is connected to the first muffler space 111, the other end of the second flow hole 140 is connected to the third muffler space 131, the inner peripheral wall of the second muffler 400, the second sealing cover 500 and the first The bottom walls of the two high-pressure chambers 130 enclose a fourth silencer space 132, and the second silencer 400 is provided with a second air inlet hole 401, and the second air inlet hole 401 penetrates the second silencer 400 to connect the third silencer space 131 with the fourth silencer space 132. In this way, when the compressor is exhausted, the flow direction of the refrigerant is cylinder cavity-first flow hole 120-first silencer space 111-first air inlet hole 201-second silencer space 112-air outlet hole 202-first silencer space 111-second flow hole 140-third silencer space 131-second air inlet hole 401-fourth silencer space 132, and the refrigerant is silenced in the first silencer space 111, the second silencer space 112, the third silencer space 131 and the fourth silencer space 132 respectively, and the refrigerant can be silenced multiple times to reduce exhaust pulsation and vibration noise.

[0068] It should be noted that the compressor can also include a third muffler and a third sealing cover. The crankcase 100 corresponds to a 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 muffler is arranged in the third high-pressure chamber to separate the third high-pressure chamber into a fifth muffler space and a sixth muffler space. The third muffler is provided with a third air inlet hole. The fifth muffler space is connected to the sixth muffler space through the third air inlet hole. The third sealing cover is used to seal the third high-pressure chamber, and can perform multi-stage muffler on the refrigerant to reduce exhaust pulsation and reduce vibration noise.

[0069] It can be understood that at least one second silencer 400 can be configured. When one second silencer 400 is configured, the second high-pressure chamber 130 is divided into a third silencer space 131 and a fourth silencer space 132; when two second silencers 400 are configured, the two second silencers 400 are coaxially arranged, one second silencer 400 is located on the inner side of the other second silencer 400, and the second high-pressure chamber 130 is divided into a third silencer space 131 and two fourth silencer spaces 132, and the two fourth silencer spaces 132 are connected through the second air inlet hole 401 of the second silencer 400 located on the inner side, so that the refrigerant can be silenced in multiple stages; when at least three second silencers 400 are configured, at least three second silencers 400 are coaxially arranged, and adjacent fourth silencer spaces 132 are connected through the second air inlet hole 401 of the corresponding second silencer 400, so that the refrigerant can be silenced in multiple stages.

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

[0071] It should be noted that when the compressor is exhausted, the refrigerant in the cylinder cavity flows into the first silencer space 111 through the first flow hole 120. Since the first air inlet hole 201 and the first flow hole 120 are arranged relative to each other, part of the refrigerant in the first silencer space 111 can quickly flow into the second silencer space 112, and the refrigerant can be diverted to reduce the flow rate of the refrigerant, making the flow of the refrigerant more regular, thereby ensuring that the flow of the refrigerant in the first high-pressure chamber 110 is more uniform.

[0072] It is understandable that if the first air inlet 201 is arranged 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 flows directly into the third silencer space 131, and the refrigerant in the first silencer space 111 that enters the second silencer space 112 is too little, and the flow rate of the refrigerant cannot be effectively reduced.

[0073] For example Figure 5 As shown, in this embodiment, along the circumference of the first silencer 200, the first air inlet 201 and the air outlet 202 are staggered, which can avoid the refrigerant flowing into the second silencer space 112 from the first air inlet 201 from colliding with the refrigerant flowing out of the second silencer space 112 from the air outlet 202, so as to make the flow of the refrigerant 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 is beneficial to reducing exhaust pulsation.

[0075] It should be pointed out that the minimum angle between the line connecting the center of the first air inlet 201 and the center of the first silencer 200 and the line connecting the center of the air outlet 202 and the center of the first silencer 200 is θ, which satisfies: 30°≤θ≤180°, and the value of θ can be 30°, 40°, 50°, 60°, 70°, 80°, 90°, 100°, 110°, 120°, 130°, 140°, 150°, 160°, 170° and 180°, which can avoid the refrigerant flowing into the second silencer space 112 from the first air inlet 201 from colliding with the refrigerant flowing out of the second silencer 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, which is passed through the second sealing cover 500 and one end of the second exhaust pipe 620 extends into the fourth silencer space 132, so that the refrigerant in the second high-pressure chamber 130 can only be discharged after entering the fourth silencer space 132, which can avoid the situation where part of the refrigerant is discharged before entering the fourth silencer space 132, and can reduce exhaust pulsation and 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 accommodated in the fourth silencing space 132 through the second through hole 510 , which can facilitate the installation of the second exhaust pipe 620 .

[0078] It should be noted that, in this embodiment, there is no need to provide the 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 the specific structure of the first silencer 200 of the compressor in the first embodiment of the present invention, and will not be described in detail herein.

[0080] For example Figure 6 As shown, in this embodiment, the second silencer 400 includes a second cylinder 410 and a second flange 420. The second cylinder 410 is accommodated in the second high-pressure chamber 130, and the second cylinder 410 is coaxially arranged with the second high-pressure chamber 130. One end of the second cylinder 410 away from the bottom wall of the second high-pressure chamber 130 is folded outward to form a 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 clamped between the end wall of the second high-pressure chamber 130 facing the opening and the second sealing cover 500, which can facilitate the fixing of the second flange 420 to improve the installation stability of the second silencer 400.

[0081] It should be noted that along the radial direction of the second cylinder 410, the second flange 420 is folded outward, and the second flange 420 is extended 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 other 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 pointed out 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 arranged between the second flange 420 and the second sealing cover 500, and a fourth gasket 840 is arranged 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 clamped between the third gasket 830 and the fourth gasket 840.

[0083] It is understandable that the second cylinder 410 and the second flange 420 are an integrated structure, and the second cylinder 410 and the second flange 420 can be integrally formed by stamping, which can reduce the number of molds, thereby reducing the production and manufacturing costs of the molds, thereby reducing the production and manufacturing costs of the compressor, which is not limited here. Of course, in 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, along the radial direction of the second cylinder 410, the minimum thickness of the second cylinder 410 is T3, satisfying: 1mm≤T3≤3mm. On the one hand, the structural strength of the second cylinder 410 can be ensured, and on the other hand, the second cylinder 410 can be prevented from occupying too much space in the second high-pressure chamber 130, so as to ensure that the second high-pressure chamber 130 has good sound-absorbing performance.

[0085] It should be noted that if T3 is less than 1 mm, 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 is exhausted, the second high-pressure chamber 130 is a high-pressure environment, and the second cylinder 410 is prone to collapse or bend, resulting in a reduction in the service life of the second cylinder 410, and it cannot be used in a high-pressure environment for a long time; the space in the second high-pressure chamber 130 is limited. If T3 is greater than 3 mm, the minimum thickness of the second cylinder 410 is too large, and the effectively utilized space in the second high-pressure chamber 130 is reduced, resulting in poor silencing effect of the compressor.

[0086] It should be pointed out 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, without limitation herein.

[0087] In this embodiment, along the axial direction of the second cylinder 410, the minimum thickness of the second flange 420 is T4, satisfying: 1mm≤T4≤2mm. On the one hand, the structural strength of the second flange 420 can be ensured, and on the other hand, the overall height of the compressor can be reduced.

[0088] It should be noted that if T4 is less than 1 mm, the minimum thickness of the second flange 420 is too small, the structural strength of the second flange 420 is reduced, and when the compressor is exhausted, the second high-pressure chamber 130 is a high-pressure environment. Cracks are easily generated at the connection position between the second cylinder 410 and the second flange 420, resulting in a reduction in the service life of the second silencer 400; if T4 is greater than 2 mm, the minimum thickness of the second flange 420 is too large, and the effectively utilized space in the second high-pressure chamber 130 is reduced, resulting in poor silencer effect of the compressor.

[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 through a second fastener 720. The second fastener 720 is a bolt or a screw, so that a stable connection is achieved between the second sealing cover 500 and the crankcase 100, 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 smaller than the minimum inner diameter of the second muffler 400. On the one hand, it can avoid interference between the second boss 160 and the second muffler 400 to facilitate the assembly of the second muffler 400. On the other hand, it can ensure that the fourth muffler space 132 has a large enough space to effectively buffer the refrigerant entering the fourth muffler space 132.

[0091] It should be noted that, for example Figure 7 As shown, the minimum inner diameter of the second silencer 400 is D2, which satisfies: 7mm≤D2≤10mm, which can avoid the interference between the second boss 160 and the second silencer 400, and ensure that the fourth silencer space 132 has a large enough space. If D2 is less than 7mm, in order to avoid the interference between the second boss 160 and the second silencer 400, the maximum width of the second boss 160 must also be less than 7mm, and the second boss 150 is threadedly connected with the second fastener 720. When the maximum width of the second boss 160 is less than 7mm, the structural strength of the second boss 160 is 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 silencer 400 is too large, the space in the second high-pressure chamber 130 is limited, and the volume of the third silencer space 131 is 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, without limitation herein.

[0093] Reference Figure 8 , Fig. 9 , Figure 8 Schematic diagram of the change of exhaust pressure of the second embodiment of the present invention and the comparative example, Fig. 9 The figure is a flow chart of the refrigerant in the second embodiment of the present invention and the comparative example. In the comparative example, the compressor does not include the first muffler 200 and the second muffler 400, and the refrigerant in the first high-pressure chamber 110 directly enters the second high-pressure chamber 130 through the second flow 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 exhaust pressure of the compressor of the second embodiment with that of the compressor of the comparative example, it is found that the exhaust pressure of the compressor of the second embodiment has a significant improvement at the trough, the trough stabilization speed is faster and the pressure here is higher. The three cycle data are processed and the standard deviation is obtained for comparison. The standard deviation of the exhaust pressure of the compressor of the comparative example is 305.15Pa, and the standard deviation of the exhaust pressure of the compressor of the second embodiment is 290.96Pa. The overall exhaust pressure is reduced by about 5%.

[0095] Depend on Fig. 9It can be seen that the flow of the refrigerant in the comparative compressor is very turbulent, with the maximum flow velocity reaching 53.95 m / s, and a darker area appears in the second high-pressure chamber 130 of the comparative compressor, and the refrigerant flows concentratedly in this area; while the flow of the refrigerant in the compressor of the second embodiment is obviously more regular, and no darker area appears in the second high-pressure chamber 130 of the compressor of the second embodiment, and the refrigerant flows more evenly in the second flow hole 140, with the maximum flow velocity being only 44.59 m / s. Therefore, the provision of the first muffler 200 and the second muffler 400 is beneficial to reducing exhaust pulsation.

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

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

[0098] An embodiment of the present invention is described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above embodiment, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A compressor, characterized in that include: case; A crankcase, installed in the housing, the crankcase having a cylinder cavity, a first high-pressure cavity and a first flow hole, wherein the first flow hole is configured to connect the cylinder cavity and the first high-pressure cavity; A first sealing cover, sealing the opening of the first high-pressure chamber; A first silencer is arranged in the first high-pressure chamber, and the outer peripheral wall of the first silencer and the inner peripheral wall of the first high-pressure chamber jointly define a first silencer space, the lower end of the peripheral wall of the first silencer abuts against the bottom wall of the first high-pressure chamber, and the upper end of the peripheral wall of the first silencer abuts against the first sealing cover, the inner peripheral wall of the first silencer, the first sealing cover and the bottom wall of the first high-pressure chamber together form a second silencer space, and the first silencer is provided with a first air inlet hole, and the first silencer space is connected to the second silencer space through the first air inlet hole.

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 provided in the first cylinder, the first flange is provided at one end of the first cylinder close to the first sealing cover along the axial direction of the first cylinder, the first flange is arranged around the outer peripheral wall of the first cylinder, and the first flange is clamped 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 an 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, satisfying: 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 boss, the first sealing cover is connected to the first boss via a first fastener, the first cylinder is sleeved on the outer periphery of the first boss, and the lower end of the first cylinder is sealed 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 silencer is D1, which satisfies: 7mm≤D1≤10mm.

8. The compressor according to claim 1, characterized in that: 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.

9. The compressor according to claim 1, characterized in that: The crankcase has a second high-pressure chamber and a second flow hole, a second muffler is provided in the second high-pressure chamber, the crankcase is provided with a second sealing cover, the second sealing cover is sealed at the opening of the second high-pressure chamber, the first muffler is provided with an air outlet hole running through its peripheral wall, the inner peripheral wall of the second high-pressure chamber and the outer peripheral wall of the second muffler jointly define a third muffler space, the second flow hole is configured to connect the first muffler space and the third muffler space, the lower end of the peripheral wall of the first muffler abuts the bottom wall of the second high-pressure chamber, the upper end of the peripheral wall of the first muffler abuts the second sealing cover, the inner peripheral wall of the second muffler, the second sealing cover and the bottom wall of the second high-pressure chamber enclose a fourth muffler space, the second muffler is provided with a second air inlet hole, and the third muffler space is connected to the fourth muffler space through the second air inlet hole.

10. The compressor according to claim 9, characterized in that: The first air inlet hole is located on a side of the first muffler close to the first flow hole.

11. The compressor according to claim 10, characterized in that: The first air inlet and the air outlet are staggered along the circumferential direction of the first muffler.

12. The compressor according to claim 9, characterized in that: The compressor further includes a second exhaust pipe, one end of which is inserted into the second sealing cover and one end of which extends into the fourth silencing space.

13. Refrigeration equipment, characterized in that: A compressor comprising the compressor described in any one of claims 1-12.

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