Piston compressor and refrigeration equipment

Abstract

The invention relates to the technical field of compressors and discloses a piston type compressor and refrigeration equipment, the piston type compressor comprises a crankcase, a crankshaft, a connecting rod and an oil baffle part, the oil baffle part covers an eccentric shaft section and a crankshaft connecting part, an opening is formed in the peripheral wall of the oil baffle part and comprises a first opening and a second opening, the connecting rod penetrates through the first opening, and the connecting rod penetrates through the second opening; the second opening is communicated with the end, away from the first penetrating hole in the axial direction of the crankshaft, of the first opening and comprises a first opening part and a second opening part which are communicated in the axial direction of the crankshaft, the first opening part is opposite to the piston, and the second opening part is opposite to the side wall, away from the first penetrating hole in the axial direction of the crankshaft, of the air cylinder cavity. The circumferential width of the second opening part is reduced in the direction away from the first opening, and the maximum circumferential width of the second opening part is smaller than or equal to the minimum circumferential width of the first opening part. Therefore, the piston type compressor can solve the problem of high high-frequency oil spitting quantity, and the lubricating effect on the piston and the cylinder head part under the low-frequency working condition is not easily influenced.

Description

Technical Field

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

[0002] With the continuous development of society, refrigerators have become an indispensable household appliance. As a core component of refrigerators, the performance requirements for compressors are becoming increasingly higher. The compressor oil circulation system is an important guarantee for the normal operation of the compressor and plays a key role in its performance and reliability. During operation, the lubricating oil is drawn from the oil sump at the bottom of the compressor to the top of the crankshaft through the rotation of the crankshaft. It is then ejected through the oil sling holes on the crankshaft to provide good lubrication for the piston, connecting rod, cylinder and other components inside the compressor, thereby reducing friction and wear.

[0003] However, in the related art, the above oil-splitting method is difficult to control under high-frequency and low-frequency operating conditions of the compressor, especially under high-frequency operating conditions, which easily leads to a high oil discharge volume and affects the performance coefficient of the compressor. Summary of the Invention

[0004] 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 piston compressor that can improve the problem of high oil discharge at high frequencies while not significantly affecting the lubrication effect on the piston and cylinder head under low-frequency conditions.

[0005] According to the first embodiment of the present invention, a piston compressor includes: a crankcase, the crankcase includes a main body and a cylinder head, the main body is formed with a first through-hole, and the cylinder head has a cylinder cavity; a crankshaft, the crankshaft includes a main shaft section and an eccentric shaft section, the main shaft section is rotatably matched with the first through-hole, and the eccentric shaft section is formed with an oil-swinging hole penetrating its outer surface; a connecting rod, the two ends of the connecting rod respectively have a crankshaft connecting part and a piston connecting part, the crankshaft connecting part is sleeved outside the eccentric shaft section and avoids the oil-swinging hole, and the piston connecting part is connected to the piston arranged in the cylinder cavity; an oil baffle, the oil baffle cover is arranged outside the eccentric shaft section and the crankshaft connecting part, and the oil baffle The circumferential wall of the component is formed with the opening opposite to one end of the cylinder head in the direction of piston movement, the opening including a first opening and a second opening, the connecting rod is passed through the first opening, the second opening is connected to one end of the first opening away from the first through-hole in the axial direction of the crankshaft, and includes a first mouth and a second mouth connected along the axial direction of the crankshaft, the first mouth is opposite to the piston, the second mouth is opposite to the cylinder wall on one side of the cylinder cavity away from the first through-hole in the axial direction of the crankshaft, the circumferential width of the second mouth decreases in the direction away from the first opening, and the circumferential maximum width of the second mouth is less than or equal to the circumferential minimum width of the first mouth.

[0006] According to the piston compressor of the embodiment of the present invention, an oil baffle cover is arranged outside the eccentric shaft section and the crankshaft connection part, and the first mouth is opposite to the piston, the second mouth is opposite to the corresponding cylinder wall of the cylinder cavity, and the circumferential width of the second mouth decreases in the direction away from the first opening, and the circumferential maximum width of the second mouth is less than or equal to the circumferential minimum width of the first mouth, so that the setting of the oil baffle is not likely to limit the amount of oil supplied under low-frequency operation conditions. At the same time, the oil baffle can limit the amount of oil supplied under high-frequency operation conditions, improve the problem of high high-frequency oil discharge, thereby improving the performance of the piston compressor, and regardless of high-frequency operation or low-frequency operation, the oil baffle can make the lubricating oil be directed to the piston and cylinder head, thereby achieving reliable lubrication of the piston and cylinder head.

[0007] In some embodiments, at least one of the circumferential end edges of the second mouth portion extends spirally in the axial direction.

[0008] In some embodiments, the circumferential width of the first mouth portion remains unchanged or decreases in a direction away from the first opening, the minimum circumferential width of the first mouth portion is greater than the maximum circumferential width of the second mouth portion; and / or the maximum circumferential width of the first mouth portion is less than or equal to the circumferential width of the first opening.

[0009] In some embodiments, the cylinder cavity is formed with a through-notch on the cylinder wall on the side away from the first through-hole in the axial direction of the crankshaft, and the notch passes through the cylinder wall of the cylinder cavity at one end facing the second opening, so that the notch is opposite to the second mouth, and a portion of the piston is suitable for being exposed through the notch, and the maximum circumferential width of the second mouth is 0.9 to 1.1 times the width of the notch of the notch.

[0010] In some embodiments, a first exhaust chamber and a second exhaust chamber are formed on the main body, the first exhaust chamber is connected to the air outlet of the cylinder chamber, the second exhaust chamber is connected to the first exhaust chamber through a connecting channel, one axial end of the second exhaust chamber is connected to an inner exhaust pipe, and the connecting channel extends obliquely from the first exhaust chamber toward the second exhaust chamber toward the other axial end of the second exhaust chamber.

[0011] In some embodiments, the peripheral wall of the oil baffle is open at one end facing the crankcase, and the oil baffle also has an end wall, which is connected to the end of the peripheral wall of the oil baffle away from the crankcase, and the end wall closes the corresponding end of the peripheral wall.

[0012] In some embodiments, the outer peripheral wall of the eccentric shaft segment includes a first wall portion and a second wall portion, the first wall portion cooperates with the crankshaft connecting portion, the second wall portion is located on the side of the first wall portion away from the main shaft segment and opposite to the first mouth portion, the oil-swinging hole passes through the second wall portion to form a first oil outlet, and the first oil outlet is opposite to the first mouth portion; and / or, the end of the eccentric shaft segment away from the main shaft segment does not exceed the cylinder wall on the side of the cylinder cavity away from the through hole, and the oil-swinging hole passes through the end face of the eccentric shaft segment away from the main shaft segment to form a second oil outlet.

[0013] In some embodiments, the oil baffle is fixed to the crankcase.

[0014] In some embodiments, the oil blocking member is disposed adjacent to the cylinder head, so that the piston is adapted to reciprocate through the second opening.

[0015] In some embodiments, at least one exhaust cavity is formed on the main body, and the exhaust cavity is located on the outer peripheral side of the first perforation. The exhaust cavity is directly or indirectly connected to the air outlet of the cylinder cavity, and the peripheral wall of the oil baffle is provided with a connecting arm, and the connecting arm is fixedly connected to the cavity wall of the exhaust cavity.

[0016] In some embodiments, the peripheral wall of the oil baffle is abutted against the crankcase, one end of the exhaust chamber is open and provided with a chamber cover, a fastener is passed through the chamber cover, and the fastener is threadedly connected to the crankcase so that the chamber cover sealing cover is provided at the open end of the exhaust chamber, wherein the fastener is passed through the connecting arm, and the connecting arm is clamped between the fastener and the chamber cover.

[0017] In some embodiments, the peripheral wall of the oil baffle is arranged around the portion of the crankshaft extending out of the first through-hole and is arranged adjacent to the exhaust chamber. The peripheral wall of the oil baffle is formed with a avoidance opening spaced apart from the opening, and the avoidance opening avoids the position of the crankcase corresponding to the exhaust chamber.

[0018] In some embodiments, the opening and the avoidance port both pass through one end of the circumferential wall of the oil baffle member adjacent to the first through-hole, and the circumferential wall of the oil baffle member has a first part and a second part arranged at intervals along the circumference, the first part is located between the opening and the avoidance port and is opposite to the communication position between the cylinder chamber and the exhaust chamber, the circumferential width of the first part is smaller than the circumferential width of the first opening and smaller than the circumferential width of the avoidance port, the second part is located between the opening and the avoidance port and is arranged away from the communication position between the cylinder chamber and the exhaust chamber, the circumferential width of the second part is larger than the circumferential width of the first opening and larger than the circumferential width of the avoidance port, the first part is spaced apart from the crankcase, and the second part stops at the crankcase.

[0019] In some embodiments, the peripheral wall of the oil baffle is open at one end facing the crankcase, and the oil baffle also has an end wall, which is connected to the end of the peripheral wall of the oil baffle away from the crankcase, and a third opening is formed on the end wall. On the cross section of the crankshaft, the orthographic projection of the peripheral wall of the third opening is located outside the motion trajectory of the oil outlet position of the oil throwing hole.

[0020] In some embodiments, the crankshaft also includes a balancing block, which is connected between the main shaft section and the eccentric shaft section, and / or the balancing block is connected to the end of the eccentric shaft section away from the main shaft section, the peripheral wall of the oil baffle is stopped against the crankcase, and the oil baffle cover is arranged outside the balancing block.

[0021] The refrigeration device according to the second embodiment of the present invention includes the piston compressor according to the first embodiment of the present invention.

[0022] The refrigeration equipment according to the embodiment of the present invention, by adopting the above-mentioned piston compressor, is conducive to improving the refrigeration performance of the refrigeration equipment.

[0023] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the following description of the embodiments with reference to the accompanying drawings, in which: Figure 1 is a cross-sectional view of a piston compressor according to some embodiments of the present invention; Figure 2 yes Figure 1 An enlarged view of the circled section A; Figure 3 yes Figure 1 Schematic diagram of the assembly of the crankcase, oil retainer and inner discharge pipe shown in ; Figure 4 yes Figure 3 A cross-sectional view of the crankcase, oil retainer and inner drain pipe shown in FIG; Figure 5 yes Figure 1 Schematic diagram of the assembly of the crankcase, crankshaft, connecting rod, piston, oil retainer and inner discharge pipe shown in ; Figure 6 yes Figure 1 A sectional view of a partial structure of a piston compressor shown in ; Figure 7 yes Figure 1 Schematic diagram of the oil baffle shown in ; Figure 8 yes Figure 7 Another schematic diagram of the oil retaining member shown in ; Figure 9 yes Figure 7 Another schematic diagram of the oil baffle shown in ; Figure 10 is a partial cross-sectional view of a crankshaft according to some embodiments of the present invention; Figure 11 is a partial cross-sectional view of a crankshaft according to other embodiments of the present invention; Figure 12 is a schematic diagram of a refrigeration device according to some embodiments of the present invention.

[0025] Reference numerals: Refrigeration equipment 200, piston compressor 100, Crankcase 1, main body 11, first exhaust chamber 11a, second exhaust chamber 11b, exhaust chamber 11c, first through hole 11d, communication channel 11e, cylinder head 12, cylinder chamber 12a, upper cylinder wall 12b, clearance notch 12c, air outlet 12d, Crankshaft 2, main shaft section 21, oil guide groove 211, eccentric shaft section 22, oil-slinging hole 22a, first oil outlet 22b, second oil outlet 22c, first wall portion 221, second wall portion 222, balance block 23, Connecting rod 3, crankshaft connecting part 31, piston connecting part 32, Oil baffle 4, peripheral wall 41, opening 41a, first opening 41b, second opening 41c, first opening 41d, second opening 41e, avoidance opening 41f, first portion 411, second portion 412, end wall 42, third opening 42a, connecting arm 43, third through hole 43a, Piston 5 , piston pin 51 , cavity cover 6 , second through-hole 6 a , fastener 7 , sealing gasket 8 , inner row pipe 9 , housing 10 . DETAILED DESCRIPTION

[0026] The following describes embodiments of the present invention in detail. Examples of the embodiments 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 intended only to explain the present invention and are not to be construed as limiting the present invention.

[0027] The disclosure below provides many different embodiments or examples for realizing different structures of the present invention. In order to simplify the disclosure of the present invention, the components and settings of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. In addition, the present invention may repeat reference numbers and / or letters in different examples. This repetition is for the purpose of simplicity and clarity and does not in itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the present invention provides examples of various specific processes and materials, but those skilled in the art will appreciate the applicability of other processes and / or the use of other materials.

[0028] In the description of the embodiments of this application, the term "and / or" is simply a description of the association relationship between associated objects, indicating that three relationships can exist. For example, A and / or B can represent the following three situations: A exists alone, A and B exist simultaneously, and B exists alone. In addition, the character " / " in this document generally indicates that the associated objects are in an "or" relationship.

[0029] Hereinafter, a piston compressor 100 according to an embodiment of a first aspect of the present invention will be described with reference to the accompanying drawings.

[0030] like Figure 1 and Figure 2 、 Figure 10 、 Figure 11As shown, the piston compressor 100 includes a crankcase 1 and a crankshaft 2. The crankcase 1 includes a main body 11 and a cylinder head 12. The main body 11 is formed with a first through-hole 11d. The cylinder head 12 has a cylinder cavity 12a. The cylinder cavity 12a is provided with a piston 5. The piston 5 can reciprocate in the cylinder cavity 12a to achieve gas compression. The crankshaft 2 includes a main shaft section 21 and an eccentric shaft section 22. The main shaft section 21 is rotatably engaged with the first through-hole 11d. The eccentric shaft section 22 is formed with an oil-swinging hole 22a passing through its outer surface. During the rotation of the crankshaft 2 relative to the crankcase 1, the lubricating oil in the eccentric shaft section 22 rotates with the eccentric shaft section 22, and under the action of centrifugal force, the lubricating oil is thrown to the surroundings of the eccentric shaft section 22 through the oil-swinging hole 22a.

[0031] The piston compressor 100 includes a connecting rod 3, and the two ends of the connecting rod 3 respectively have a crankshaft connecting portion 31 and a piston connecting portion 32. The piston connecting portion 32 is connected to the piston 5 provided in the cylinder chamber 12a. The crankshaft connecting portion 31 is sleeved outside the eccentric shaft segment 22, and the crankshaft connecting portion 31 avoids the oil-slinging hole 22a. Therefore, the crankshaft connecting portion 31 can rotate with the eccentric shaft segment 22, and the crankshaft connecting portion 31 will not block or close the oil outlet position of the oil-slinging hole 22a (for example, the oil-slinging hole 22a is formed on the outer surface of the eccentric shaft segment 22). The oil outlet is formed, and the crankshaft connecting part 31 does not block the oil outlet), the oil-slinging hole 22a is not formed on the wall surface of the eccentric shaft segment 22 that cooperates with the crankshaft connecting part 31, so that the lubricating oil in the eccentric shaft segment 22 can be smoothly spun out through the oil-slinging hole 22a, and a part of the spun lubricating oil can be spun toward the piston 5 and / or the cylinder head 12 to lubricate the contact surface between the piston 5 and the cylinder head 12, which is beneficial to reducing the friction between the piston 5 and the cylinder head 12 and facilitating reducing the heat generation of the piston compressor 100.

[0032] It can be understood that the main shaft section 21 and the eccentric shaft section 22 can be arranged in sequence along the axial direction of the crankshaft 2, and the central axis of the main shaft section 21 is parallel to the central axis of the eccentric shaft section 22 and is arranged at intervals. When the crankshaft 2 rotates, the eccentric shaft section 22 rotates eccentrically to drive the piston 5 to reciprocate through the connecting rod 3.

[0033] like Figure 2 、 Figure 4 and Figure 7As shown, the piston compressor 100 further includes an oil baffle 4, which is provided outside the eccentric shaft segment 22 and the crankshaft connecting portion 31. The peripheral wall 41 of the oil baffle 4 is formed with an opening 41a. The opening 41a penetrates the peripheral wall 41 along the thickness direction of the peripheral wall 41 of the oil baffle 4, so that the inner and outer sides of the peripheral wall 41 are connected through the opening 41a. The lubricating oil thrown out from the oil-throwing hole 22a to the periphery of the eccentric shaft segment 22 can be partially blocked by the peripheral wall 41, and a portion can be thrown out through the opening 41a. One end of the cylinder head 12 in the movement direction F1 of the piston 5 is opposite to the opening 41a, so The oil thrown out through the opening 41a is conveniently directionally thrown toward the above-mentioned end of the cylinder head 12, so as to improve the lubrication effect on the friction pair between the piston 5 and the cylinder head 12, and is also helpful to control the approximate area where the lubricating oil is thrown out. Compared with the scheme in which the lubricating oil is thrown out freely and randomly around, the method of directional oil throwing toward the piston 5 and the cylinder head 12 of the present application is beneficial to reduce the amount of lubricating oil entering the intake and exhaust system of the piston compressor 100 to a certain extent, thereby helping to improve the cooling capacity of the piston compressor 100 and improve the refrigeration capacity of the piston compressor 100.

[0034] It can be understood that the end of the cylinder head 12 facing the oil baffle 4 is open, while the end of the cylinder head 12 facing away from the oil baffle 4 is provided with a cylinder cover, so that the above-mentioned directional oil throwing in this application can achieve better lubrication effect on the piston 5 and the cylinder head 12 using less oil.

[0035] Among them, the opening 41a includes a first opening 41b and a second opening 41c. The connecting rod 3 is passed through the first opening 41b. The first opening 41b can avoid the movement of the connecting rod 3 so that the oil baffle 4 does not interfere with the connecting rod 3. The second opening 41c is connected to the end of the first opening 41b away from the first through hole 11d in the axial direction of the crankshaft 2.

[0036] like Figure 2 、 Figure 4 and Figure 7 As shown, the second opening 41c includes a first mouth portion 41d and a second mouth portion 41e which are connected along the axial direction of the crankshaft 2. The first mouth portion 41d is opposite to the piston 5, and the second mouth portion 41e is opposite to the cylinder wall of the cylinder cavity 12a on the side away from the first through hole 11d in the axial direction of the crankshaft 2. The first mouth portion 41d is arranged between the second mouth portion 41e and the first opening 41b, and the circumferential width of the second mouth portion 41e decreases in the direction away from the first opening 41b. The circumferential maximum width of the second mouth portion 41e is less than or equal to the circumferential minimum width of the first mouth portion 41d.

[0037] It can be understood that the first mouth 41d and the second mouth 41e are both hollowed out, and the peripheral wall 41 of the oil baffle 4 can be roughly extended into a ring shape ("ring" should be understood in a broad sense, that is, not limited to a circular ring, a cone, or a truncated cone. For example, it can also be a polygonal ring, a polygonal cone, etc.), so that the oil baffle 4 can be covered outside the eccentric shaft segment 22 and the crankshaft connection portion 31. The circumferential width of the second mouth 41e can be understood as the width of the second mouth 41e in the extension direction of the peripheral wall 41 of the oil baffle 4. The extension direction of the peripheral wall 41 of the oil baffle 4 can be basically consistent with the circumference of the main shaft segment 21, or, the extension direction of the peripheral wall 41 of the oil baffle 4 is basically consistent with the circumference of the eccentric shaft segment 22, and so on.

[0038] Therefore, the portion of the peripheral wall 41 of the oil baffle 4 surrounding the second opening 41e can block the lubricating oil thrown out at different axial positions to different degrees, and the axial position of the thrown lubricating oil is related to the rotational speed of the crankshaft 2. In other words, the axial position of the thrown lubricating oil is related to the operating frequency of the piston compressor 100. The portion of the peripheral wall 41 of the oil baffle 4 surrounding the second opening 41c can block the lubricating oil thrown out at different operating frequencies to different degrees, so as to improve the problem of excessive high-frequency oil discharge while taking into account the low-frequency oil discharge, which is beneficial to improving the operating performance of the piston compressor 100.

[0039] Taking the axial direction of the crankshaft 2 as an example, the eccentric shaft section 22 is provided on the upper side of the main shaft section 21, and the cylinder chamber 12a is arranged in the horizontal direction so that the piston 5 can reciprocate horizontally in the cylinder chamber 12a. The two ends of the axial direction of the cylinder chamber 12a (the axial direction of the cylinder chamber 12a is consistent with the movement direction of the piston 5) are respectively the first end and the second end. Relative to the second end, the first end is adjacent to the eccentric shaft section 22, and the opening 41a is horizontally opposite to the first end, which means that the first end and at least part of the opening 41a are basically at the same height position; and the opening 41a includes a first opening 41b and a second opening 41c, and the first end is adjacent to the eccentric shaft section 22. The two openings 41c are connected on the upper side of the first opening 41b, and the second opening 41c includes a first mouth portion 41d and a second mouth portion 41e which are connected to each other in an upper and lower manner. The first mouth portion 41d is connected between the second mouth portion 41e and the first opening 41b, so that the second mouth portion 41e is located on the upper side of the first mouth portion 41d, the first mouth portion 41d is horizontally opposite to the piston 5, and the second mouth portion 41e is horizontally opposite to the upper cylinder wall 12b of the cylinder chamber 12a, the circumferential width t2 of the second mouth portion 41e decreases from bottom to top, and the circumferential width of the lower end of the second mouth portion 41e is less than or equal to the minimum circumferential width of the first mouth portion 41d.When the piston compressor 100 is running at a low frequency, the oil line thrown out from the oil-throwing hole 22a is low, and part of the lubricating oil is thrown out through the first mouth portion 41d. The circumferential width of the first mouth portion 41d is relatively large, and the first mouth portion 41d provides a large flow space for the lubricating oil to pass through. The oil baffle 4 does not play a role or basically does not play a role in blocking the lubricating oil that is directed to the piston 5. The oil baffle 4 is not likely to limit the amount of oil supplied under low-frequency working conditions, so that the setting of the oil baffle 4 is not likely to affect the lubricating effect of the lubricating oil on the piston 5 and the cylinder head 12, thereby achieving the purpose of controlling the piston 5. The reliable lubrication effect of the fitting between the plug 5 and the cylinder head 12; when the piston compressor 100 is running at a high frequency, the oil line thrown out from the oil-throwing hole 22a is higher, and part of the lubricating oil is thrown out through the second mouth portion 41e. The circumferential width of the second mouth portion 41e is smaller than that of the first mouth portion 41d, and the flow space provided by the second mouth portion 41e for the lubricating oil to pass through is smaller. The oil baffle 4 has a greater blocking effect on the lubricating oil thrown toward the cylinder head 12, so as to limit the amount of lubricating oil thrown toward the cylinder head 12 and the piston 5, thereby reducing the amount of lubricating oil entering through the cylinder cavity 12a. The amount of lubricating oil in the suction and exhaust system of the piston compressor 100 can effectively reduce the amount of oil discharged during high-frequency operation of the piston compressor 100. At the same time, since the occupation of the refrigerant space by the lubricating oil is reduced, the influence of the lubricating oil on the refrigerant temperature at both ends of the suction and exhaust of the piston compressor 100 is reduced, the cooling capacity and refrigeration capacity of the piston compressor 100 can be improved. Moreover, too much lubricating oil in the refrigerant will increase the viscous resistance of the refrigerant. Therefore, the above-mentioned setting can also appropriately improve the cooling capacity of the piston compressor 100 to a certain extent. COP (i.e. coefficient of performance); moreover, when the piston compressor 100 operates at different high frequencies, if the operating frequency of the piston compressor 100 is higher, the oil line thrown out from the oil-throwing hole 22a under certain conditions will basically be higher, and the circumferential width of the second mouth 41e at the height position corresponding to the oil line will also be smaller. The blocking effect of the oil baffle 4 on the lubricating oil thrown toward the cylinder head 12 can be further enhanced, reducing the possibility of the oil discharge amount increasing with the increase of the operating frequency under high-frequency working conditions, so as to take into account the performance of the piston compressor 100 under different high-frequency working conditions.

[0040] As an example, the oil baffle 4 can be fixedly connected to the crankshaft connection portion 31 so that the oil baffle 4 moves with the crankshaft connection portion 31; alternatively, the oil baffle 4 can be fixedly connected to the crankcase 1 so that the oil baffle 4 is stationary relative to the crankcase 1, while the eccentric shaft segment 22 and the crankshaft connection portion 31 can move relative to the oil baffle 4. Regardless of how the oil baffle 4 is fixed, it is sufficient that the oil baffle 4 can be positioned outside the eccentric shaft segment 22 and the crankshaft connection portion 31, the connecting rod 3 is inserted into the first opening 41b, the first opening 41d is opposite the piston 5, and the second opening 41e is opposite the corresponding cylinder wall of the cylinder chamber 12a.

[0041] Furthermore, because the first port 41d is opposite the piston 5 and communicates with the first opening 41b, the risk of interference between the connecting rod 3 and the oil baffle 4 is further reduced. Furthermore, even if the oil baffle 4 is positioned relatively close to the cylinder head 12 or the piston 5 moves to its closest position relative to the oil baffle 4 (for example, if the oil baffle 4 is fixedly connected to the crankcase 1), the first port 41d and the first opening 41b can provide a certain clearance from the piston 5, thereby reducing the risk of interference between the oil baffle 4 and the piston 5. Of course, if the oil baffle 4 moves with the crankshaft connection 31, the spacing between the oil baffle 4 and the piston 5 is substantially constant, and the dimensions of the first port 41d and the first opening 41b do not need to be considered to clear the piston 5. The first port 41d can still lubricate the piston 5 and the cylinder head 12.

[0042] As an example, the bottom of the piston compressor 100 has an oil pool, and an oil guide groove 211 is formed on the main shaft segment 21. The oil guide groove 211 can be arranged on the outer peripheral wall of the main shaft segment 21 and extend in an axial spiral along the main shaft segment 21. The oil guide groove 211 is connected with the oil throwing hole 22a. For example, the oil guide groove 211 is connected with the oil throwing hole 22a inside the crankshaft 2. When the crankshaft 2 rotates, the centrifugal force generated by the oil guide groove 211 of the main shaft segment 21 draws the lubricating oil at the bottom upward, and then the lubricating oil is pumped to the oil throwing hole 22a of the eccentric shaft segment 22 through the oil guide groove 211 of the main shaft segment 21. Under the action of the centrifugal force generated by the rotation of the crankshaft 2, the lubricating oil in the oil throwing hole 22a is thrown out of the eccentric shaft segment 22 and thrown to the surroundings.

[0043] For example, the width of the second opening 41 c in the circumferential direction of the crankshaft 2 decreases linearly or nonlinearly (eg, decreases in a stepwise manner) in a direction away from the first opening 41 b .

[0044] It is understood that the piston compressor 100 also includes a housing 10, within which the crankcase 1, crankshaft 2, connecting rod 3, and oil retainer 4 are all disposed. The housing 10 serves as an external protective cover for the piston compressor 100, providing not only mechanical support but also a seal to prevent external impurities from entering the interior of the piston compressor 100. The piston compressor 100 also includes a drive structure (not shown) disposed within the housing 10 and connected to the main shaft section 21 so as to drive the crankshaft 2 to rotate. The central axis of the main shaft section 21 serves as the rotational axis of the crankshaft 2. The central axis of the eccentric shaft section 22 is parallel to and spaced apart from the central axis of the main shaft section 21. Driven by the drive structure, the eccentric shaft section 22 rotates eccentrically, thereby driving the piston 5 to reciprocate via the connecting rod 3. For example, if the drive structure includes a drive motor, the drive motor includes a stator and a rotor. The crankcase 1 is connected to the stator and / or the housing 10 is connected to the stator, and the rotor is connected to the crankshaft 2 to achieve rotation of the crankshaft 2.

[0045] According to the piston compressor 100 of the embodiment of the present invention, an oil baffle 4 is provided to cover the outside of the eccentric shaft section 22 and the crankshaft connecting part 31, and the first mouth 41d is opposite to the piston 5, and the second mouth 41e is opposite to the corresponding cylinder wall of the cylinder cavity 12a, and the circumferential width of the second mouth 41e decreases in the direction away from the first opening 41b, and the circumferential maximum width of the second mouth 41e is less than or equal to the circumferential minimum width of the first mouth 41d, so that the setting of the oil baffle 4 is not likely to limit the amount of oil supplied under low-frequency operation conditions. At the same time, the oil baffle 4 can limit the amount of oil supplied under high-frequency operation conditions, improve the problem of high high-frequency oil discharge, thereby improving the performance of the piston compressor 100, and regardless of high-frequency operation or low-frequency operation, the oil baffle 4 can make the lubricating oil directionally thrown to the piston 5 and the cylinder head 12, so as to achieve reliable lubrication of the piston 5 and the cylinder head 12, and it is not easy for the oil baffle 4 to excessively restrict the amount of lubricating oil thrown to the piston 5 and the cylinder head 12 in order to achieve directional oil throwing. In addition, the oil baffle 4 has a simple structure and is not likely to interfere with other components of the piston compressor 100. Under certain conditions, the oil baffle 4 can be directly installed on the crankcase 1 or the crankshaft connection part 31 without adjusting other components of the piston compressor 100, which is beneficial to reducing design costs.

[0046] Alternatively, as Figure 1 、 Figure 2 、 Figure 4 As shown, the edges of the second opening 41e at both ends in the axial direction of the crankshaft 2 are flush with the inner and outer walls of the corresponding cylinder walls, respectively. For example, if the axial direction of the crankshaft 2 is the vertical direction, the upper edge of the second opening 41e is flush with the outer wall of the upper cylinder wall 12b of the cylinder cavity 12a, and the lower edge of the second opening 41e is flush with the inner wall of the upper cylinder wall 12b of the cylinder cavity 12a. Of course, in other embodiments, the upper edge of the second opening 41e can also be located above the outer wall of the upper cylinder wall 12b of the cylinder cavity 12a.

[0047] It is understood that the second opening 41e can pass through the upper end of the peripheral wall 41 of the oil retaining member 4, or, as shown in FIG. Figure 2 、 Figure 4 and Figure 7 As shown, the second opening 41 e is spaced apart from the upper end of the peripheral wall 41 of the oil baffle 4 .

[0048] In some embodiments, as Figure 7 As shown, at least one of the circumferential end edges of the second mouth portion 41e extends spirally along the axial direction of the oil retaining member 4, so the second mouth portion 41e is roughly formed into a trapezoidal mouth or a triangular mouth. The structure of the second mouth portion 41e is simple and easy to process.

[0049] It can be understood that the axial direction of the oil baffle 4 can be the axial direction of the peripheral wall 41 of the oil baffle 4 , and the axial direction of the peripheral wall 41 of the oil baffle 4 can be consistent with the axial direction of the crankshaft 2 .

[0050] For example, Figure 7 As shown, the circumferential edges of the second opening 41e extend spirally along the axial direction of the oil retaining member 4, and the spiral directions of the circumferential edges of the second opening 41e are opposite, and the spiral angles of the two edges are substantially equal, so that the second opening 41e is roughly formed into an isosceles trapezoid or an isosceles triangle. The second opening 41e has a certain degree of symmetry, which facilitates better alignment of the second opening 41e with the corresponding cylinder wall of the cylinder cavity 12a, thereby achieving lubrication of the piston 5 and the cylinder head 12 with a smaller amount of oil under high-frequency operating conditions. Of course, the spiral directions of the circumferential edges of the second opening 41e can also be the same, and / or the spiral angles of the circumferential edges of the second opening 41e can be different; or, one of the circumferential edges of the second opening 41e can extend spirally, and the other can extend linearly along the axial direction of the oil retaining member 4.

[0051] In some embodiments, as Figure 7 and Figure 8 As shown, the circumferential width t1 of the first mouth portion 41d remains unchanged or decreases in the direction away from the first opening 41b, which facilitates the processing of the first mouth portion 41d. Among them, the circumferential minimum width of the first mouth portion 41d is greater than the circumferential maximum width of the second mouth portion 41e, and the circumferential widths of the first mouth portion 41d and the second mouth portion 41e suddenly change at the intersection. The circumferential widths of the first mouth portion 41d and the second mouth portion 41e have a relatively obvious difference, which is convenient for taking into account the low-frequency operation of the piston compressor 100 so that the first mouth portion 41d can provide sufficient circulation space for the lubricating oil to be thrown out, and at the same time, the second mouth portion 41e can reliably block the lubricating oil and limit the throwing to the cylinder head under the high-frequency operation of the piston compressor 100. 12 of lubricating oil; and / or, the maximum circumferential width of the first mouth portion 41d is less than or equal to the circumferential width t4 of the first opening 41b, so that the first opening 41b has a suitable circumferential size to achieve at least avoidance of the connecting rod 3. At the same time, under the low-frequency operation condition of the piston compressor 100, even if some lubricating oil is thrown out through the first opening 41b, the first opening 41b can also provide it with sufficient circulation space, so as to further weaken the obstruction of the oil baffle 4 to the lubricating oil thrown toward the piston 5 and the cylinder head 12 under the low-frequency condition, thereby achieving reliable lubrication of the piston 5 and the cylinder head 12.

[0052] For example, Figure 7 and Figure 8As shown, the circumferential width of the first opening 41d decreases from bottom to top. The circumferential width of the upper end of the first opening 41d is greater than the circumferential width of the lower end of the second opening 41e. The circumferential width of the lower end of the first opening 41d is equal to the circumferential width of the first opening 41b. The first opening 41d facilitates the transition between the first opening 41b and the second opening 41e, better accommodating the size variation between the circumferential widths of the first opening 41b and the second opening 41e. The variation trend of the circumferential width of the first opening 41d is consistent with that of the second opening 41e, facilitating processing. The circumferential width of the first opening 41b can be constant along the axial direction, but is not limited to this. For example, the circumferential width of the first opening 41b can decrease toward the second opening 41c. In this case, the circumferential width of the lower end of the first opening 41d can be less than or equal to the maximum circumferential width of the first opening 41b. Of course, the circumferential width of the first mouth portion 41d may also remain unchanged along the axial direction. In this case, the circumferential width of the first opening 41b may remain unchanged along the axial direction, or decrease toward the second opening 41c.

[0053] Optionally, at least one of the two circumferential edges of the first mouth portion 41d extends spirally along the axial direction of the oil retaining member 4, so that the circumferential width of the first mouth portion 41d decreases in a direction away from the first opening 41b.

[0054] In some embodiments, as Figure 1 、 Figure 2 、 Figure 7 and Figure 8 As shown, the side of the first opening 41b away from the second opening 41c penetrates the peripheral wall 41 of the oil baffle 4. By way of example, the first opening 41b penetrates the lower end of the peripheral wall 41 of the oil baffle 4, facilitating smoother positioning of the peripheral wall 41 of the oil baffle 4 outside the eccentric shaft segment 22 and the crankshaft connecting portion 31, thereby facilitating assembly of the piston compressor 100. For example, the connecting rod 3 and the eccentric shaft segment 22 can be assembled first, and then the oil baffle 4 can be axially positioned outside the eccentric shaft segment 22 and the crankshaft connecting portion 31. Of course, in other embodiments, the first opening 41b may not penetrate the lower end of the peripheral wall 41 of the oil baffle 4. In this case, the connecting rod 3 can be first passed through the first opening 41b and then assembled with the eccentric shaft segment 22 within the oil baffle 4.

[0055] In some embodiments, as Figure 2-Figure 5As shown, a through-hole 12c is formed in the cylinder wall of the cylinder chamber 12a on the side axially away from the first through-hole 11d of the crankshaft 2. The through-hole 12c extends through the cylinder wall of the cylinder chamber 12a at one end facing the second opening 41c, such that the through-hole 12c faces the second opening 41e. A portion of the piston 5 is adapted to be exposed through the through-hole 12c. As a result, a portion of the lubricating oil ejected through the opening 41a can fall into the through-hole 12c and flow onto the surface of the piston 5 during its movement, thereby lubricating the friction pair between the piston 5 and the cylinder head 12. This facilitates reliable lubrication with a relatively small amount of oil. This is particularly true under high-frequency operating conditions, where the oil baffle 4 provides relatively little space for the lubricating oil to flow. The second opening 41e faces the through-hole 12c, allowing more lubricating oil ejected from the second opening 41e to flow into the through-hole 12c. This allows reliable lubrication of the piston 5 and the cylinder head 12 while limiting the amount of oil ejected.

[0056] For example, Figure 2-Figure 5 As shown, the upper wall of the cylinder cavity 12a is formed with a clearance notch 12c, which penetrates the upper wall along the thickness direction of the upper wall, and penetrates the end of the upper cylinder wall 12b facing the second opening 41c to form a notch, so that the notch of the clearance notch 12c is opposite to the second mouth 41e; the piston 5 reciprocates in the cylinder cavity 12a and between the top dead center and the bottom dead center. When the piston 5 is at the bottom dead center, or when the piston 5 is at a position near the bottom dead center, a part of the piston 5 can be exposed through the clearance notch 12c, such as in combination with Figure 2 and Figure 5 The piston 5 is connected to the piston connecting portion 32 via a piston pin 51 , and a portion of the piston 5 that faces the oil baffle 4 and the piston pin 51 are adapted to be exposed through the clearance notch 12 c.

[0057] Alternatively, as Figure 2-Figure 5 and Figure 7 As shown, the maximum circumferential width of the second opening 41e is 0.9 to 1.1 times the slot width t3 of the clearance notch 12c. For example, the circumferential width of the lower end of the second opening 41e is 0.9 to 1.1 times the slot width t3 of the clearance notch 12c. As a result, the relative sizes of the second opening 41e and the clearance notch 12c are more appropriate, allowing the oil baffle 4 to better block lubricating oil that is flung from the oil fling hole 22a toward gas locations other than the clearance notch 12c under high-frequency operating conditions. This prevents the oil baffle 4 from weakening its oil-blocking function and directional oil-flushing effect due to an overly large second opening 41e, nor does it prevent the amount of oil flung toward the clearance notch 12c from being too small, which could limit the lubrication effect.

[0058] In some embodiments, as Figure 5 and Figure 6As shown, the main body 11 is formed with a first exhaust chamber 11a and a second exhaust chamber 11b. The first exhaust chamber 11a is connected to the outlet 12d of the cylinder chamber 12a, and the second exhaust chamber 11b is connected to the first exhaust chamber 11a via a connecting channel 11e. One axial end of the second exhaust chamber 11b is connected to the inner exhaust pipe 9. The connecting channel 11e extends obliquely from the first exhaust chamber 11a toward the second exhaust chamber 11b, toward the other axial end of the second exhaust chamber 11b. It can be seen that the location where the second exhaust chamber 11b connects to the connecting channel 11e is relatively far away from the location where the second exhaust chamber 11b connects to the inner exhaust pipe 9. At the same time, gas flowing from the connecting channel 11e toward the second exhaust chamber 11b flows away from the inner exhaust pipe 9 into the second exhaust chamber 11b, allowing the second exhaust chamber 11b to better collect and buffer the high-pressure gas and reduce airflow pulsation.

[0059] For example, Figure 6 As shown, the flow area of the connecting channel 11e decreases from the first exhaust chamber 11a toward the second exhaust chamber 11b, which is beneficial to appropriately enhance the throttling effect of the connecting channel 11e on the high-pressure airflow therein, so as to further reduce the pulsation in the airflow and help reduce the noise generated by the pulsation.

[0060] In some embodiments, as Figure 3 and Figure 7 As shown, the peripheral wall 41 of the oil baffle 4 is open at one end facing the crankcase 1, and the oil baffle 4 also has an end wall 42, which is connected to the end of the peripheral wall 41 of the oil baffle 4 away from the crankcase 1, which is beneficial to improving the structural strength of the oil baffle 4; the end wall 42 closes the corresponding end of the peripheral wall 41. For example, the end wall 42 is connected to the upper end of the peripheral wall 41, and the end wall 42 closes a part of the upper end of the peripheral wall 41, then a third opening 42a is formed on the end wall 42, and part of the lubricating oil thrown out from the oil-throwing hole 22a can be thrown to the inner wall of the shell 10 of the piston compressor 100 through the third opening 42a to perform contact heat dissipation on the shell 10.

[0061] In some embodiments, as Figure 2 and Figure 10 As shown, the outer peripheral wall of the eccentric shaft segment 22 includes a first wall portion 221 and a second wall portion 222. The first wall portion 221 cooperates with the crankshaft connecting portion 31, and the second wall portion 222 is located on the side of the first wall portion 221 away from the main shaft segment 21, and the second wall portion 222 is opposite to the first opening portion 41d. The oil-slinging hole 22a passes through the second wall portion 222 to form a first oil outlet 22b. The crankshaft connecting portion 31 does not block the first oil outlet 22b. The first oil outlet 22b is opposite to the first opening portion 41d, so that the oil slinging out from the first oil outlet 22b can be better directed to the first opening portion 41d; and / or, Figure 2 、 Figure 10 and Figure 11As shown, the end of the eccentric shaft segment 22 away from the main shaft segment 21 does not extend beyond the cylinder wall on the side of the cylinder cavity 12a away from the perforation, and the oil-swinging hole 22a penetrates the end surface of the eccentric shaft segment 22 away from the main shaft segment 21 to form a second oil outlet 22c. The crankshaft connecting part 31 does not block the second oil outlet 22c, so that the lubricating oil is easily spun out from the second oil outlet 22c to the surroundings, so that part of the lubricating oil is spun toward the piston 5 and the cylinder head 12.

[0062] Exemplarily, the oil-swinging hole 22a passes through the upper end face of the eccentric shaft segment 22, and the upper end face of the eccentric shaft segment 22 is located between the outer wall surface and the inner wall surface of the upper cylinder wall 12b of the cylinder cavity 12a in the up-down direction (including the upper end face of the eccentric shaft segment 22 being flush with the outer wall surface or the inner wall surface of the upper cylinder wall 12b), or the upper end face of the eccentric shaft segment 22 is located between the inner wall surface of the upper cylinder wall 12b of the cylinder cavity 12a and the upper end face of the connecting rod 3 in the up-down direction.

[0063] In some embodiments, as Figure 3 、 Figure 5 and Figure 6 As shown, the oil baffle 4 is fixed to the crankcase 1. It is understood that the oil baffle 4 can be directly fixedly connected to the crankcase 1, or the oil baffle 4 can be indirectly fixedly connected to the crankcase 1 through other components. It is sufficient to keep the oil baffle 4 stationary relative to the crankcase 1. In this case, the eccentric shaft segment 22 and the crankshaft connecting portion 31 can move relative to the oil baffle 4 within the oil baffle 4.

[0064] Therefore, the oil baffle 4 is not fixed to the crankshaft 2 and the connecting rod 3, and does not move with the crankshaft 2 and the connecting rod 3. Therefore, when the piston compressor 100 is not provided with the oil baffle 4, the original dynamic balance setting is not easy to need to redesign the dynamic platform due to the addition of the oil baffle 4, which is beneficial to reducing the design cost. In other words, the dynamic balance design of the piston compressor 100 does not need to consider the oil baffle 4; at the same time, the oil baffle 4 does not need to be driven to move by the drive structure connected to the crankshaft 2, and the load of the drive structure will not be increased due to the addition of the oil baffle 4, and no higher requirements will be put forward for the drive structure; moreover, the oil baffle 4 does not move relative to the cylinder head 12, so the relative position of the oil baffle 4 and the cylinder head 12 It remains unchanged at all times, which is beneficial to improving the directional oil throwing effect of throwing the oil toward the piston 5 and the cylinder head 12 through the second opening 41c, and is not prone to excessive restrictions on the directional oil throwing effect due to the relative position between the second port and the cylinder head 12 changing at any time due to the movement of the oil baffle 4; in addition, it is convenient to arrange the oil baffle 4 closer to the cylinder head 12 within the allowed arrangement space, which is beneficial to reducing the distance between the first port 41d and the piston 5 and reducing the distance between the second port 41e and the cylinder head 12, so that the lubricating oil thrown out from the opening 41a can be lubricated to the piston 5 and the cylinder head 12 in a more timely and directional manner, which is beneficial to improving the directional oil throwing effect on the cylinder head 12 and the piston 5.

[0065] Alternatively, as Figure 2 、 Figure 3 and Figure 7 As shown, the oil baffle 4 is arranged near the cylinder head 12 so that the piston 5 is suitable for reciprocating through the second opening 41c. At this time, the oil baffle 4 is close to the cylinder head 12, which is conducive to improving the directional oil throwing effect, and the oil baffle 4 will not affect the reciprocating motion of the piston 5.

[0066] For example, Figure 2 As shown, the piston 5 reciprocates in the cylinder chamber 12a between the top dead center and the bottom dead center. When the piston 5 is at the bottom dead center, or when the piston 5 is at a position near the bottom dead center, the piston 5 can pass through the second opening 41c. The piston 5 moves toward the top dead center and can disengage from the second opening 41c.

[0067] In some embodiments, as Figure 3 、 Figure 5 and Figure 6 As shown, at least one exhaust cavity 11c is formed in the main body 11. The exhaust cavity 11c is located on the outer periphery of the first through-hole 11d and is in direct or indirect communication with the gas outlet 12d of the cylinder cavity 12a. For example, if there is a single exhaust cavity 11c, the exhaust cavity 11c is in direct or indirect communication with the gas outlet 12d of the cylinder cavity 12a. If there are multiple exhaust cavities 11c, one exhaust cavity 11c adjacent to the cylinder cavity 12a is in direct or indirect communication with the gas outlet 12d of the cylinder cavity 12a, while the remaining cylinder cavities 12a can be indirectly connected to the gas outlet 12d of the cylinder cavity 12a via the exhaust cavity 11c. Adjacent exhaust cavities 11c can be arranged in a communication manner. Therefore, the exhaust chamber 11c is connected between the air outlet 12d of the cylinder chamber 12a and the exhaust pipe of the piston compressor 100, serving as a "transition space" connecting the cylinder chamber 12a and the exhaust pipe, which can concentrate and buffer the high-pressure pulsating gas discharged from the cylinder chamber 12a. When the pulsating airflow enters the larger exhaust chamber 11c, the airflow velocity decreases and the pressure fluctuation is weakened, thereby reducing the impact on the subsequent pipeline system, which is beneficial to reducing vibration and noise.

[0068] Among them, the peripheral wall 41 of the oil baffle 4 is provided with a connecting arm 43, and the connecting arm 43 is fixedly connected to the cavity wall of the exhaust chamber 11c. Therefore, while realizing the fixed installation of the oil baffle 4, the oil baffle 4 is not easy to affect the flow path of the gas in the piston compressor 100, and it is convenient to simplify the structure of the crankcase 1 without having to separately process a fixing structure for fixing the oil baffle 4.

[0069] For example, in Figure 3 、 Figure 5 and Figure 7In the example, the connecting arm 43 extends in a straight line, one end of the connecting arm 43 is integrally connected to the peripheral wall 41 of the oil retaining member 4, and the other end of the connecting arm 43 is connected to the cavity wall of the exhaust cavity 11c. Of course, the structure of the connecting arm 43 is not limited to this.

[0070] In some embodiments, as Figure 2-Figure 4 and Figure 6 As shown, the peripheral wall 41 of the oil retaining member 4 abuts against the crankcase 1, one end of the exhaust chamber 11c is open and a chamber cover 6 is provided at the long open end of the exhaust chamber 11c, and a fastener 7 (such as a screw, etc.) is passed through the chamber cover 6. The fastener 7 is threadedly connected to the crankcase 1 so that the chamber cover 6 is sealed and arranged at the open end of the exhaust chamber 11c. A second through-hole 6a for the fastener 7 to pass through is formed on the chamber cover 6. Under the fastening action of the fastener 7, the exhaust chamber 11c is sealed and easy to assemble. Moreover, the above-mentioned setting of the exhaust chamber 11c facilitates the processing of the crankcase 1. For example, the crankcase 1 is an integrally formed part, and one end of the exhaust chamber 11c is open, which facilitates the processing feasibility of the crankcase 1.

[0071] The fastener 7 is inserted through the connecting arm 43, which is sandwiched between the fastener 7 and the cavity cover 6. A third through-hole 43a is formed on the connecting arm 43 for the fastener 7 to pass through. Under the tightening action of the fastener 7, the portion surrounding the edge of the third through-hole 43a is sandwiched between the fastener 7 and the cavity cover 6, thereby securing the oil baffle 4. Simultaneously, because the peripheral wall 41 of the oil baffle 4 abuts against the crankcase 1, the portion surrounding the edge of the third through-hole 43a can provide a certain degree of compression and sealing for the gap between the fastener 7 and the second through-hole 6a, thereby improving the seal between the fastener 7 and the cavity cover 6. It can be understood that the fastener 7 can both seal the exhaust chamber 11c with the cavity cover 6 and install the oil baffle 4. Furthermore, the installation of the oil baffle 4 is unlikely to excessively affect the sealing of the exhaust chamber 11c, thus achieving "multiple uses for one item." The piston compressor 100 has a simple structure and low cost.

[0072] It should be noted that the sealing method between the fastener 7 and the cavity cover 6 is not limited. For example, at least one of the following sealing methods can be used: achieving sealing through compression between the wall of the second through-hole 6a and the fastener 7; providing a seal between the fastener 7 and the cavity cover 6; providing a sealing gasket 8 between the connecting arm 43 and the cavity cover 6; or providing a sealing gasket 8 on both sides of the connecting arm 43 along the length of the fastener 7. Optionally, the sealing gasket 8 is a metal member.

[0073] It can be understood that when there are multiple exhaust cavities 11c, if there is only one connecting arm 43, the connecting arm 43 can be connected to the cavity wall of any exhaust cavity 11c; or, if there are multiple connecting arms 43, each connecting arm 43 is connected to the cavity wall of the corresponding exhaust cavity 11c.

[0074] In some embodiments, as Figure 3 、 Figure 4 and Figure 7 As shown, the peripheral wall 41 of the oil baffle 4 surrounds the portion of the crankshaft 2 extending beyond the first perforation 11d, and the oil baffle 4 is positioned adjacent to the exhaust chamber 11c. A relief opening 41f is formed on the peripheral wall 41 of the oil baffle 4, spaced apart from the opening 41a. The relief opening 41f is positioned away from the position of the crankcase 1 corresponding to the exhaust chamber 11c. Thus, the relief opening 41f is positioned away from the portion of the crankcase 1 wall defining the exhaust chamber 11c. If one end of the exhaust chamber 11c is open and covered with a chamber cover 6, the relief opening 41f can also be positioned away from the chamber cover 6. Thus, the oil baffle 4 can be positioned away from the exhaust chamber 11c, facilitating placement of the oil baffle 4 closer to the cylinder head 12. At the same time, the walls of the exhaust chamber 11c can provide a certain degree of shielding for the relief opening 41f, reducing the amount of oil ejected from the relief opening 41f and improving the problem of lubricating oil splashing. The shape of the relief opening 41f can be adjusted to suit the desired relief structure.

[0075] It is understood that the avoidance opening 41f can be arranged to avoid at least one exhaust cavity 11c. Figure 3 、 Figure 4 and Figure 7 As shown, there are multiple exhaust chambers 11c, and the avoidance port 41f avoids all the exhaust chambers 11c. The multiple exhaust chambers 11c are arranged in series, and the gas compressed in the cylinder chamber 12a flows through the multiple exhaust chambers 11c in sequence through the outlet 12d. The multiple exhaust chambers 11c can form a multi-level buffer, so that the pressure of the exhaust gas is more stable. If the exhaust chamber 11c is connected to an inner exhaust pipe 9, the inner exhaust pipe 9 can be connected to the exhaust pipe of the piston compressor 100, and the avoidance port 41f can be reasonably set according to the layout requirements of the inner exhaust pipe 9, so that the avoidance port 41f can also avoid the setting of the inner exhaust pipe 9; in the example of the figure, the second exhaust chamber 11b is connected to the inner exhaust pipe 9, and a part of the inner exhaust pipe 9 is bent and extended toward the oil baffle 4, and the avoidance port 41f is set to avoid the above-mentioned part of the inner exhaust pipe 9. Of course, if the inner exhaust pipe 9 is set away from the oil baffle 4 and is set around the crankcase 1, so that the inner exhaust pipe 9 is far away from the oil baffle 4, then the avoidance port 41f can be set without avoiding the inner exhaust pipe 9.

[0076] For example, Figure 2 As shown, the peripheral wall 41 of the oil baffle 4 is arranged around the portion of the crankshaft 2 that extends upward from the first through-hole 11d. If a balancing block 23 is connected between the main shaft section 21 and the eccentric shaft section 22, the peripheral wall 41 of the oil baffle 4 is arranged around the balancing block 23.

[0077] In some embodiments, as Figure 4 and Figure 7As shown, the opening 41a and the avoidance opening 41f both pass through one end of the peripheral wall 41 of the oil baffle 4 adjacent to the first through-hole 11d, so as to facilitate the installation of the oil baffle 4. For example, the oil baffle 4 can be moved close to the crankcase 1 along the axial direction of the crankshaft 2 until it reaches a predetermined position (for example, the oil baffle 4 abuts against the crankcase 1, and / or the connecting arm 43 abuts against the chamber cover 6). The peripheral wall 41 of the oil baffle 4 has a first portion 411 and a second portion 412 spaced apart along the circumferential direction, the first portion 411 being located between the opening 41a and the avoidance opening 41f and being located at a communication position between the first portion 411 and the cylinder chamber 12a and the exhaust chamber 11c. Relatively speaking, the circumferential width of the first portion 411 is smaller than the circumferential width of the first opening 41b, and the circumferential width of the first portion 411 is smaller than the circumferential width of the avoidance port 41f. The second portion 412 is located between the opening 41a and the avoidance port 41f, and the second portion 412 is arranged to face away from the communication position between the cylinder chamber 12a and the exhaust chamber 11c. The circumferential width of the second portion 412 is greater than the circumferential width of the first opening 41b, and the circumferential width of the second portion 412 is greater than the circumferential width of the avoidance port 41f. The first portion 411 is spaced apart from the crankcase 1, and the second portion 412 is stopped at the crankcase 1.

[0078] Therefore, since the second part 412 stops against the crankcase 1 and cooperates with the setting of the connecting arm 43, the oil baffle 4 can be reliably fixed, and the circumferential width of the second part 412 is relatively large and the circumferential width of the first part 411 is relatively small, which can achieve reliable stopping of the oil baffle 4 and the crankcase 1, and it is not easy to crush the second part 412. At the same time, relative to the second part 412, the first part 411 is relatively close to the connecting arm 43, and the first part 411 does not stop against the crankcase 1, which can improve the problem of the first part 411 being easily crushed, which is beneficial to taking into account the reliability and installation firmness of the oil baffle 4.

[0079] In some embodiments, as Figure 1-Figure 3 As shown, the peripheral wall 41 of the oil baffle 4 is open at one end facing the crankcase 1, and the oil baffle 4 also has an end wall 42, which is connected to the end of the peripheral wall 41 of the oil baffle 4 away from the crankcase 1, and the end wall 42 is formed with a third opening 42a, which penetrates the end wall 42 along the thickness direction of the end wall 42. Part of the lubricating oil thrown out from the oil-throwing hole 22a can be thrown to the inner wall of the shell 10 of the piston compressor 100 through the third opening 42a to perform contact heat dissipation on the shell 10.

[0080] In the cross section of the crankshaft 2, the orthographic projection of the peripheral wall 41 of the third opening 42a is located outside the trajectory of the oil outlet position of the oil-slinging hole 22a. The oil outlet position of the oil-slinging hole 22a can be understood as the oil outlet being formed on the outer surface of the eccentric shaft segment 22. In this case, in the cross section of the crankshaft 2, the orthographic projection of the peripheral wall 41 of the third opening 42a is located outside the orthographic projection of the oil outlet trajectory. Therefore, regardless of the position to which the oil outlet position of the oil-slinging hole 22a follows the movement of the eccentric shaft segment 22, the slinged lubricating oil can be more smoothly and directly spun through the third opening 42a toward the housing 10, facilitating continuous heat dissipation from the housing 10.

[0081] It can be understood that the shape of the third opening 42 a is not limited. For example, the third opening 42 a can be a circular opening, a polygonal opening (such as a square opening), etc.

[0082] As an example, the lower end of the peripheral wall 41 of the oil baffle 4 is open, and the upper end is connected to the end wall 42, and the end wall 42 is formed into an annular structure so that the end wall 42 defines a third opening 42a. In the radial direction of the crankshaft 2, the radial distance between any point on the peripheral wall 41 of the third opening 42a and the rotation axis of the crankshaft 2 is greater than the radial distance between the oil outlet and the rotation axis of the crankshaft 2.

[0083] In some embodiments, as Figure 1 and Figure 2 As shown, the crankshaft 2 further includes a balancing weight 23, which is connected between the main shaft section 21 and the eccentric shaft section 22, and / or connected to the end of the eccentric shaft section 22 away from the main shaft section 21. The peripheral wall 41 of the oil baffle 4 abuts against the crankcase 1, and the peripheral wall 41 of the oil baffle 4 abuts against the main body 11, and the oil baffle 4 is disposed outside the balancing weight 23. As a result, the oil baffle 4 is less likely to interfere with the balancing weight 23, and the oil baffle 4 can be disposed closer to the cylinder head 12 and the piston 5, which is beneficial for improving the directional oil throwing effect.

[0084] It can be understood that when the balancing block 23 is connected to the end of the eccentric shaft segment 22 away from the main shaft segment 21, the balancing block 23 also avoids the oil outlet position of the oil-swinging hole 22a. For example, the balancing block 23 is sleeved on the outside of the eccentric shaft segment 22, and the oil-swinging hole 22a passes through the end face of the eccentric shaft segment 22 away from the main shaft segment 21 to form a second oil outlet 22c.

[0085] In some embodiments, the piston compressor 100 also includes a muffler, which is connected upstream of the air inlet of the cylinder chamber 12a. The air flow first flows through the muffler and then flows to the cylinder chamber 12a. Then, in the movement direction of the piston 5, the muffler is arranged on the side of the cylinder head 12 away from the oil baffle 4, and in the circumferential direction of the crankshaft 2, the muffler is located on the lower side of the cylinder head 12. The setting of the oil baffle 4 is conducive to reducing the amount of oil flowing into the muffler.

[0086] The inventors of the present application conducted high-frequency operating condition and low-frequency operating condition tests on multiple groups of comparative examples and multiple groups of embodiments of the present application, and the test results are shown in Tables 1 and 2 below. The test method is well known to those skilled in the art. Comparative examples 1-9 do not use oil baffles. Embodiments 1-9 are based on comparative examples 1-9 and additionally include an oil baffle 4. Other conditions are the same, and the average oil discharge volume is the average of the maximum values of the three time periods.

[0087] As can be clearly seen from Table 1, under the high-frequency operating condition of 75Hz, the average oil discharge per hour of the control example is 7.7515ml, while the average oil discharge per hour of the embodiment is 3.2276ml, which is significantly lower than that of the control example and has basically decreased by 58.4%. As can be clearly seen from Table 2, under the high-frequency operating condition of 75Hz, the cooling capacity of the embodiment is improved by 3.7W, the COP is improved by 0.003, and the operating noise is reduced by 0.3dB relative to the control example. Under the low-frequency operating condition of 27Hz, the cooling capacity of the embodiment is improved by 1.1W, the COP is improved by 0.018, and the operating noise is reduced by 0.36dB relative to the control example. It can be seen that the provision of the oil baffle 4 in the embodiment of the present application can not only improve the problem of high-frequency oil discharge, but also improve the cooling capacity and reduce the operating noise to a certain extent.

[0088] Table 1 Comparison of oil discharge test results of comparative example and embodiment under high frequency operation conditions

[0089] Table 2 Comparison of performance test results of comparative examples and examples under high frequency operation conditions and low frequency operation conditions

[0090] According to the refrigeration device 200 of the second embodiment of the present invention, Figure 12 As shown, it includes a piston compressor 100 according to the embodiment of the first aspect of the present invention. The piston compressor 100 is used in a refrigerant circulation system of a refrigeration device 200 to provide power for the refrigeration cycle.

[0091] The refrigeration device 200 according to the embodiment of the present invention, by adopting the above-mentioned piston compressor 100, is conducive to improving the refrigeration performance of the refrigeration device 200.

[0092] It is worth noting that the type of the refrigeration device 200 according to the embodiment of the present application is not limited. For example, the refrigeration device 200 can be a refrigerator, a freezer, a freezer, a cold storage, or an ice maker, etc.

[0093] Other structures and operations of the refrigeration device 200 according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail here.

[0094] In addition, it should be noted that the various specific technical features described in the above specific embodiments can be combined in any suitable manner unless there is any contradiction. In order to avoid unnecessary repetition, the present application will not further describe various possible combinations. In addition, the various different embodiments of the present application can also be arbitrarily combined, as long as they do not violate the concept of the present application, they should also be regarded as the content disclosed in the present application.

[0095] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "vertical", "horizontal", "top", "bottom", "inside", "outside", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0096] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0097] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative uses of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0098] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A piston compressor, characterized in that: include: A crankcase, the crankcase comprising a main body and a cylinder head, the main body being formed with a first through-hole, and the cylinder head having a cylinder cavity therein; a crankshaft, the crankshaft comprising a main shaft section and an eccentric shaft section, the main shaft section being rotatably engaged with the first through-hole, the eccentric shaft section being formed with an oil-slinging hole penetrating an outer surface thereof; A connecting rod, wherein both ends of the connecting rod respectively have a crankshaft connecting portion and a piston connecting portion, the crankshaft connecting portion is sleeved outside the eccentric shaft section and is arranged to avoid the oil-slinging hole, and the piston connecting portion is connected to a piston provided in the cylinder cavity; An oil baffle, the oil baffle cover is arranged outside the eccentric shaft section and the crankshaft connecting part, and the peripheral wall of the oil baffle is formed with an opening opposite to one end of the cylinder head in the direction of piston movement, the opening includes a first opening and a second opening, the connecting rod is passed through the first opening, the second opening is connected to the end of the first opening away from the first through-hole in the axial direction of the crankshaft, and includes a first mouth and a second mouth arranged in communication along the axial direction of the crankshaft, the first mouth is opposite to the piston, and the second mouth is opposite to the cylinder wall on the side of the cylinder cavity away from the first through-hole in the axial direction of the crankshaft, the circumferential width of the second mouth decreases in the direction away from the first opening, and the circumferential maximum width of the second mouth is less than or equal to the circumferential minimum width of the first mouth.

2. The piston compressor according to claim 1, characterized in that At least one of the circumferential end edges of the second opening portion extends spirally in the axial direction.

3. The piston compressor according to claim 1, wherein The circumferential width of the first mouth portion remains constant or decreases in a direction away from the first opening, The minimum circumferential width of the first opening is greater than the maximum circumferential width of the second opening; and / or, The maximum circumferential width of the first mouth portion is smaller than or equal to the circumferential width of the first opening.

4. The piston compressor according to claim 1, wherein A through clearance notch is formed in the cylinder wall of the cylinder chamber on a side away from the first through hole in the axial direction of the crankshaft. The clearance notch penetrates the cylinder wall of the cylinder chamber at one end facing the second opening, so that the clearance notch is opposite to the second opening, and a portion of the piston is suitable for being exposed through the clearance notch. The maximum circumferential width of the second opening is 0.9 to 1.1 times the width of the notch of the clearance gap.

5. The piston compressor according to claim 1, characterized in that The main body is formed with a first exhaust chamber and a second exhaust chamber. The first exhaust chamber is connected to the air outlet of the cylinder chamber. The second exhaust chamber is connected to the first exhaust chamber through a connecting passage. One axial end of the second exhaust chamber is connected to an inner exhaust pipe. The communication channel extends obliquely from the first exhaust chamber toward the second exhaust chamber toward the other axial end of the second exhaust chamber.

6. The piston compressor according to claim 1, wherein The peripheral wall of the oil baffle is open at one end facing the crankcase, and the oil baffle also has an end wall, which is connected to the end of the peripheral wall of the oil baffle away from the crankcase, and the end wall closes the corresponding end of the peripheral wall.

7. The piston compressor according to claim 1, wherein The outer peripheral wall of the eccentric shaft segment includes a first wall portion and a second wall portion, the first wall portion cooperates with the crankshaft connecting portion, the second wall portion is located on a side of the first wall portion away from the main shaft segment and opposite to the first opening portion, the oil-slinging hole penetrates the second wall portion to form a first oil outlet, and the first oil outlet is opposite to the first opening portion; and / or, The end of the eccentric shaft segment away from the main shaft segment does not exceed the cylinder wall of the cylinder cavity away from the through hole, and the oil-swinging hole penetrates the end surface of the eccentric shaft segment away from the main shaft segment to form a second oil outlet.

8. The piston compressor according to any one of claims 1 to 7, characterized in that The oil baffle is fixed to the crankcase.

9. The piston compressor according to claim 8, characterized in that The oil blocking member is disposed adjacent to the cylinder head so that the piston is adapted to reciprocate through the second opening.

10. The piston compressor according to claim 8, characterized in that At least one exhaust cavity is formed on the main body, and the exhaust cavity is located on the outer peripheral side of the first through-hole. The exhaust cavity is directly or indirectly connected to the air outlet of the cylinder cavity. The peripheral wall of the oil baffle is provided with a connecting arm, and the connecting arm is fixedly connected to the cavity wall of the exhaust cavity.

11. The piston compressor according to claim 10, characterized in that The peripheral wall of the oil baffle is stopped against the crankcase, one end of the exhaust chamber is open and provided with a chamber cover, a fastener is passed through the chamber cover, and the fastener is threadedly connected to the crankcase so that the chamber cover sealing cover is arranged on the open end of the exhaust chamber. Wherein, the fastener passes through the connecting arm, and the connecting arm is clamped between the fastener and the cavity cover.

12. The piston compressor according to claim 10, characterized in that The peripheral wall of the oil baffle is arranged around the portion of the crankshaft extending out of the first through-hole and is arranged adjacent to the exhaust chamber. The peripheral wall of the oil baffle is formed with a avoidance opening spaced apart from the opening, and the avoidance opening avoids the position of the crankcase corresponding to the exhaust chamber.

13. The piston compressor according to claim 12, characterized in that The opening and the avoidance opening both pass through one end of the peripheral wall of the oil baffle member adjacent to the first through-hole. The circumferential wall of the oil baffle has a first part and a second part arranged at intervals along the circumferential direction, the first part is located between the opening and the avoidance port and is opposite to the communication position between the cylinder chamber and the exhaust chamber, the circumferential width of the first part is smaller than the circumferential width of the first opening and smaller than the circumferential width of the avoidance port, the second part is located between the opening and the avoidance port and is arranged away from the communication position between the cylinder chamber and the exhaust chamber, the circumferential width of the second part is larger than the circumferential width of the first opening and larger than the circumferential width of the avoidance port, the first part is spaced apart from the crankcase, and the second part stops at the crankcase.

14. The piston compressor according to claim 8, characterized in that The peripheral wall of the oil baffle is open at one end facing the crankcase, and the oil baffle also has an end wall, which is connected to the end of the peripheral wall of the oil baffle away from the crankcase, and a third opening is formed on the end wall. On the cross section of the crankshaft, the orthographic projection of the peripheral wall of the third opening is located outside the movement trajectory of the oil outlet position of the oil-slinging hole.

15. The piston compressor according to claim 8, characterized in that The crankshaft also includes a balancing block, which is connected between the main shaft section and the eccentric shaft section, and / or the balancing block is connected to the end of the eccentric shaft section away from the main shaft section. The peripheral wall of the oil baffle is stopped against the crankcase, and the oil baffle cover is arranged outside the balancing block.

16. A refrigeration device, characterized in that: Comprising a piston compressor according to any one of claims 1-15.

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