Reciprocating compressors and refrigeration equipment

Abstract

This invention relates to the field of compressor technology and discloses a reciprocating compressor and a refrigeration device. The reciprocating compressor includes a crankcase, a crankshaft, a connecting rod, and an oil baffle. The oil baffle covers the eccentric shaft section and the crankshaft connection portion. An opening is formed on the peripheral wall of the oil baffle, including a first opening and a second opening. The connecting rod passes through the first opening. The second opening connects to the end of the first opening in the crankshaft axial direction away from the first through hole and includes a first port and a second port connected in the crankshaft axial direction. The first port is opposite to the piston, and the second port is opposite to the cylinder wall of the cylinder chamber in the crankshaft axial direction away from the first through hole. The circumferential width of the second port decreases in the direction away from the first opening, and the maximum circumferential width of the second port is less than or equal to the minimum circumferential width of the first port. Therefore, the reciprocating compressor can improve the problem of high oil discharge at high frequencies and is less likely to affect the lubrication effect on the piston and cylinder head under low-frequency operating conditions.

Description

Technical Field

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

[0002] With the continuous development of society, refrigerators have become an indispensable household appliance. As the core component of refrigerators, the performance requirements for compressors are becoming increasingly stringent. The compressor oil circulation system is a crucial guarantee for the normal operation of the compressor, playing a key role in its performance and reliability. During compressor operation, lubricating oil can rise from the bottom oil sump to the top of the crankshaft through the crankshaft's rotation, and then be thrown outwards through the oil slingers on the crankshaft. This provides good lubrication for internal components such as pistons, connecting rods, and cylinders, reducing friction and wear.

[0003] However, in related technologies, the above-mentioned oil slinging method is not easy to control under high-frequency and low-frequency operating conditions of the compressor. In particular, under high-frequency operating conditions, the amount of oil discharged is likely to be high, which will affect the performance coefficient of the compressor. Summary of the Invention

[0004] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes a piston compressor that can improve the problem of high oil discharge at high frequencies and does not easily affect the lubrication effect on the piston and cylinder head under low-frequency operating conditions.

[0005] According to a first aspect of the present invention, a piston compressor includes: a crankcase comprising a main body and a cylinder head, the main body having a first through hole, and the cylinder head having a cylinder cavity; a crankshaft comprising a main shaft section and an eccentric shaft section, the main shaft section being rotatably fitted with the first through hole, and the eccentric shaft section having an oil slinger hole penetrating its outer surface; a connecting rod having a crankshaft connecting portion and a piston connecting portion at each end, the crankshaft connecting portion being sleeved outside the eccentric shaft section and disposed to avoid the oil slinger hole, and the piston connecting portion being connected to a piston disposed in the cylinder cavity; and an oil baffle covering the eccentric shaft section and the crankshaft connecting portion, the oil baffle... The peripheral wall of the component has 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 passes through the first opening. The second opening communicates with the end of the first opening in the axial direction of the crankshaft away from the first through hole and includes a first opening and a second opening that are connected in the axial direction of the crankshaft. The first opening is opposite to the piston, and the second opening is opposite to the cylinder wall of the cylinder chamber in the axial direction of the crankshaft away from the first through hole. The circumferential width of the second opening decreases in the direction away from the first opening, and the maximum circumferential width of the second opening is less than or equal to the minimum circumferential width of the first opening.

[0006] According to an embodiment of the reciprocating compressor of the present invention, an oil baffle is provided outside the eccentric shaft section and the crankshaft connection, with the first opening facing the piston and the second opening facing the corresponding cylinder wall of the cylinder chamber. The circumferential width of the second opening decreases in the direction away from the first opening, and the maximum circumferential width of the second opening is less than or equal to the minimum circumferential width of the first opening. This makes it less likely that the oil baffle will limit the amount of oil supplied under low-frequency operating conditions. At the same time, the oil baffle can limit the amount of oil supplied under high-frequency operating conditions, improve the problem of high oil discharge at high frequencies, and thus improve the performance of the reciprocating compressor. Moreover, regardless of whether it is high-frequency or low-frequency operation, the oil baffle can direct the lubricating oil 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 opening extends spirally along the axial direction.

[0008] In some embodiments, the circumferential width of the first opening remains unchanged or decreases in the 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 opening is less than or equal to the circumferential width of the first opening.

[0009] In some embodiments, the cylinder cavity has a through clearance notch formed on the side of the cylinder wall away from the first perforation in the axial direction of the crankshaft. The clearance notch penetrates the end of the cylinder wall of the cylinder cavity facing the second opening, so that the clearance notch is opposite to the second opening. A portion of the piston is adapted to be exposed through the clearance notch. The maximum circumferential width of the second opening is 0.9 to 1.1 times the slot width of the clearance 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 outlet of the cylinder chamber. The second exhaust chamber is connected to the first exhaust chamber through a connecting channel. An inner exhaust pipe is connected to one axial end of the second exhaust chamber. 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 connected to the end of the peripheral wall of the oil baffle away from the crankcase, the end wall closing a portion of 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 mates with the crankshaft connection portion. The second wall portion is located on the side of the first wall portion away from the main shaft segment and is opposite to the first opening. The oil slinger hole penetrates the second wall portion to form a first oil outlet, which is opposite to the first opening. And / or, the end of the eccentric shaft segment away from the main shaft segment does not extend beyond the cylinder wall of the cylinder cavity away from the perforation. The oil slinger hole penetrates 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 baffle is disposed adjacent to the cylinder head to adapt the piston to reciprocate through the second opening.

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

[0016] In some embodiments, the peripheral wall of the oil baffle abuts against the crankcase, one end of the exhaust chamber is open and has a chamber cover, a fastener is threaded through the chamber cover and is threadedly connected to the crankcase so that the chamber cover is sealed at 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 chamber cover.

[0017] In some embodiments, the peripheral wall of the oil baffle is disposed around the portion of the crankshaft extending out of the first perforation and adjacent to the exhaust chamber. The peripheral wall of the oil baffle is formed with a clearance opening spaced apart from the opening, the clearance opening avoiding the position of the crankcase corresponding to the exhaust chamber.

[0018] In some embodiments, both the opening and the clearance opening penetrate through one end of the peripheral wall of the oil baffle adjacent to the first through hole. The peripheral wall of the oil baffle has a first portion and a second portion spaced apart circumferentially. The first portion is located between the opening and the clearance opening and is opposite to the communication position between the cylinder chamber and the exhaust chamber. The circumferential width of the first portion is smaller than the circumferential width of the first opening and smaller than the circumferential width of the clearance opening. The second portion is located between the opening and the clearance opening and is disposed away from the communication position between the cylinder chamber and the exhaust chamber. The circumferential width of the second portion is larger than the circumferential width of the first opening and larger than the circumferential width of the clearance opening. The first portion is spaced apart from the crankcase, and the second portion abuts against 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 connected to the end of the peripheral wall of the oil baffle away from the crankcase. The end wall forms a third opening, and 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 slinger.

[0020] In some embodiments, the crankshaft further includes a balance block connected between the main shaft section and the eccentric shaft section, and / or the balance block is connected to the end of the eccentric shaft section away from the main shaft section, the peripheral wall of the oil baffle abuts against the crankcase, and the oil baffle is disposed outside the balance block.

[0021] A refrigeration device according to a second aspect of the present invention includes a reciprocating compressor according to the first aspect of the present invention described above.

[0022] According to embodiments of the present invention, the use of the above-described piston compressor in the refrigeration equipment improves the refrigeration performance of the refrigeration equipment.

[0023] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0024] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0025] Figure 1 This is a cross-sectional view of a piston compressor according to some embodiments of the present invention;

[0026] Figure 2 yes Figure 1 An enlarged view of part A, shown in the center circle;

[0027] Figure 3 yes Figure 1 The diagram shows the assembly of the crankcase, oil baffle, and inner manifold.

[0028] Figure 4 yes Figure 3 The cross-sectional view of the crankcase, oil baffle and inner manifold shown;

[0029] Figure 5 yes Figure 1 The diagram shows an assembly of the crankcase, crankshaft, connecting rod, piston, oil baffle, and inner manifold.

[0030] Figure 6 yes Figure 1 A cross-sectional view of a partial structure of a piston compressor shown in the figure;

[0031] Figure 7 yes Figure 1 A schematic diagram of the oil baffle shown;

[0032] Figure 8 yes Figure 7 Another schematic diagram of the oil baffle shown;

[0033] Figure 9 yes Figure 7 Another schematic diagram of the oil baffle shown;

[0034] Figure 10 This is a partial cross-sectional view of a crankshaft according to some embodiments of the present invention;

[0035] Figure 11 This is a partial cross-sectional view of a crankshaft according to other embodiments of the present invention;

[0036] Figure 12 This is a schematic diagram of a refrigeration device according to some embodiments of the present invention.

[0037] Figure label:

[0038] Refrigeration equipment 200, reciprocating compressor 100

[0039] Crankcase 1, main body 11, first exhaust chamber 11a, second exhaust chamber 11b, exhaust chamber 11c, first through hole 11d, connecting channel 11e, cylinder head 12, cylinder chamber 12a, upper cylinder wall 12b, clearance notch 12c, exhaust port 12d.

[0040] Crankshaft 2, main shaft section 21, oil guide groove 211, eccentric shaft section 22, oil slinger hole 22a, first oil outlet 22b, second oil outlet 22c, first wall portion 221, second wall portion 222, balance block 23.

[0041] Connecting rod 3, crankshaft connecting part 31, piston connecting part 32

[0042] Oil baffle 4, peripheral wall 41, opening 41a, first opening 41b, second opening 41c, first opening 41d, second opening 41e, clearance opening 41f, first part 411, second part 412, end wall 42, third opening 42a, connecting arm 43, third through hole 43a.

[0043] Piston 5, piston pin 51, cavity cover 6, second perforation 6a, fastener 7, sealing gasket 8, inner pipe 9, housing 10. Detailed Implementation

[0044] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0045] The following disclosure provides numerous different embodiments or examples for implementing various structures of the invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. Additionally, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0046] In the description of the embodiments in this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0047] Hereinafter, with reference to the accompanying drawings, a piston compressor 100 according to a first aspect embodiment of the present invention will be described.

[0048] like Figure 1 and Figure 2 , Figure 10 , Figure 11 As 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. A first through hole 11d is formed on the main body 11. The cylinder head 12 has a cylinder chamber 12a. A piston 5 is provided in the cylinder chamber 12a. The piston 5 can reciprocate in the cylinder chamber 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 fitted with the first through hole 11d. The eccentric shaft section 22 has an oil slinger hole 22a that penetrates 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, is thrown to the surrounding area of ​​the eccentric shaft section 22 through the oil slinger hole 22a.

[0049] The reciprocating compressor 100 includes a connecting rod 3, with a crankshaft connecting portion 31 and a piston connecting portion 32 at each end. The piston connecting portion 32 is connected to a piston 5 located in the cylinder chamber 12a. The crankshaft connecting portion 31 is sleeved on the outside of the eccentric shaft section 22 and is configured to avoid the oil slinger hole 22a. Thus, the crankshaft connecting portion 31 can rotate with the eccentric shaft section 22, and the crankshaft connecting portion 31 will not obstruct or close the oil outlet position of the oil slinger hole 22a (for example, the oil slinger hole 22a is formed on the outer surface of the eccentric shaft section 22). If the oil outlet is not blocked by the crankshaft connection 31, then the oil slinger 22a is not formed on the wall surface of the eccentric shaft section 22 that mates with the crankshaft connection 31, so that the lubricating oil in the eccentric shaft section 22 can be smoothly thrown out through the oil slinger 22a. Part of the thrown-out lubricating oil can be thrown towards the piston 5 and / or the cylinder head 12 to lubricate the contact surface between the piston 5 and the cylinder head 12, which helps to reduce the friction between the piston 5 and the cylinder head 12 and facilitates the reduction of the heat generation of the piston compressor 100.

[0050] It is understood that the main shaft section 21 and the eccentric shaft section 22 can be arranged sequentially along the axial direction of the crankshaft 2. The central axis of the main shaft section 21 is parallel to and spaced apart from the central axis of the eccentric shaft section 22. When the crankshaft 2 rotates, the eccentric shaft section 22 rotates eccentrically, thereby driving the piston 5 to reciprocate through the connecting rod 3.

[0051] like Figure 2 , Figure 4 and Figure 7 As shown, the piston compressor 100 also includes an oil baffle 4, which covers the eccentric shaft section 22 and the crankshaft connection 31. The peripheral wall 41 of the oil baffle 4 has an opening 41a that extends through the peripheral wall 41 along its thickness direction, allowing the inner and outer sides of the peripheral wall 41 to communicate. Thus, some of the lubricating oil thrown from the oil slinger hole 22a towards the eccentric shaft section 22 can be blocked by the peripheral wall 41, while some can be thrown out through the opening 41a. The end of the cylinder head 12 in the piston 5's movement direction F1 is opposite to the opening 41a. The oil thrown out through the opening 41a is directed towards the aforementioned end of the cylinder head 12, thereby improving the lubrication effect on the friction pair between the piston 5 and the cylinder head 12. At the same time, it is beneficial to control the approximate area where the lubricating oil is thrown out. Compared with the scheme where the lubricating oil is thrown out freely in all directions, the method of directional oil throwing towards the piston 5 and the cylinder head 12 in this 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 improving the cooling capacity and refrigeration ability of the piston compressor 100.

[0052] It is understood that the end of the cylinder head 12 facing the oil baffle 4 is open, while the end of the cylinder head 12 away from the oil baffle 4 is provided with a cylinder cover. Thus, the directional oil throwing described in this application can achieve a better lubrication effect on the piston 5 and the cylinder head 12 with a smaller amount of oil.

[0053] The opening 41a includes a first opening 41b and a second opening 41c. The connecting rod 3 passes 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 that is away from the first through hole 11d in the axial direction of the crankshaft 2.

[0054] like Figure 2 , Figure 4 and Figure 7 As shown, the second opening 41c includes a first opening 41d and a second opening 41e that are connected along the axial direction of the crankshaft 2. The first opening 41d is opposite to the piston 5, and the second opening 41e is opposite to the cylinder wall of the cylinder chamber 12a on the side away from the first through hole 11d in the axial direction of the crankshaft 2. The first opening 41d is located between the second opening 41e and the first opening 41b. The circumferential width of the second opening 41e decreases in the direction away from the first opening 41b, and the maximum circumferential width of the second opening 41e is less than or equal to the minimum circumferential width of the first opening 41d.

[0055] It is understood that both the first opening 41d and the second opening 41e are hollowed out, and the peripheral wall 41 of the oil baffle 4 can be extended into a ring shape ("ring shape" is interpreted in a broad sense, that is, it is not limited to a circular ring, a cone shape, or a frustum shape, but can also be a polygonal ring, a polygonal cone, etc.) so that the oil baffle 4 can cover the eccentric shaft section 22 and the crankshaft connecting part 31. The circumferential width of the second opening 41e can be understood as the width of the second opening 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 circumferential direction of the main shaft section 21, or the extension direction of the peripheral wall 41 of the oil baffle 4 can be basically consistent with the circumferential direction of the eccentric shaft section 22, etc.

[0056] 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 varying degrees. The axial position of the thrown-out lubricating oil is related to the rotational speed of the crankshaft 2. In other words, the axial position of the thrown-out lubricating oil is related to the operating frequency of the piston compressor 100. Thus, 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 varying degrees. This is to improve the problem of excessive oil discharge at high frequencies while taking into account the amount of oil added at low frequencies, which is beneficial to improving the operating performance of the piston compressor 100.

[0057] Taking the crankshaft 2's axial direction as vertical as an example, the eccentric shaft section 22 is located above the main shaft section 21, and the cylinder chamber 12a is arranged horizontally so that the piston 5 can reciprocate horizontally within the cylinder chamber 12a. The axial direction of the cylinder chamber 12a (the axial direction of the cylinder chamber 12a is consistent with the direction of piston 5's movement) has a first end and a second end, respectively. The first end is located adjacent to the eccentric shaft section 22 relative to the second end. Therefore, the opening 41a is horizontally opposite to the first end, meaning that at least a portion of the first end and the opening 41a are at essentially the same height. The opening 41a includes a first opening 41b and a second opening 41c. The second opening 41c connects to the upper side of the first opening 41b. The second opening 41c includes a first opening 41d and a second opening 41e that are connected vertically. The first opening 41d connects between the second opening 41e and the first opening 41b, so that the second opening 41e is located above the first opening 41d. The first opening 41d is horizontally opposite to the piston 5, and the second opening 41e is horizontally opposite to the upper cylinder wall 12b of the cylinder chamber 12a. The circumferential width t2 of the second opening 41e decreases from bottom to top, and the circumferential width of the lower end of the second opening 41e is less than or equal to the minimum circumferential width of the first opening 41d.When the reciprocating compressor 100 operates at low frequency, the oil line thrown out from the oil slinger 22a is relatively low. Some lubricating oil is thrown out through the first port 41d. The circumferential width of the first port 41d is relatively large, thus providing a large flow space for the lubricating oil to pass through. The oil baffle 4 does not play a significant or negligible role in blocking the lubricating oil directed towards the piston 5. The oil baffle 4 is unlikely to restrict the amount of oil supplied under low-frequency operating conditions. Therefore, the setting of the oil baffle 4 is unlikely to affect the lubricating effect of the lubricating oil between the piston 5 and the cylinder head 12, thereby achieving the desired lubrication effect. The reliable lubrication effect at the mating point between piston 5 and cylinder head 12; when the piston compressor 100 operates at high frequency, the oil line thrown out from the oil slinger hole 22a is relatively high, and some lubricating oil is thrown out through the second port 41e. The circumferential width of the second port 41e is relatively smaller than that of the first port 41d, so the flow space provided by the second port 41e for the lubricating oil to pass through is smaller. The oil baffle 4 plays a greater role in blocking the lubricating oil thrown towards the cylinder head 12, thereby limiting the amount of lubricating oil thrown towards the cylinder head 12 and piston 5, thus reducing the amount of lubricating oil entering through the cylinder cavity 12a. The amount of lubricating oil in the suction and discharge systems of the reciprocating compressor 100 can be reduced, thereby effectively decreasing the amount of oil discharged during high-frequency operation. Simultaneously, by reducing the space occupied by the lubricating oil in the refrigerant space, the impact of the lubricating oil on the refrigerant temperature at both the suction and discharge ends of the reciprocating compressor 100 is reduced, thus increasing the cooling capacity and refrigeration efficiency of the reciprocating compressor 100. Furthermore, excessive lubricating oil in the refrigerant increases its viscous resistance; therefore, the above-mentioned design can also appropriately improve the cooling capacity of the reciprocating compressor 100 to a certain extent. The COP (coefficient of performance) is also a factor. Furthermore, when the reciprocating compressor 100 operates at different high frequencies, if the operating frequency of the reciprocating compressor 100 is higher, the oil line thrown out from the oil slinger hole 22a will be higher under certain conditions. Then the circumferential width of the second opening 41e at the corresponding height of the oil line will be smaller. The blocking effect of the oil baffle 4 on the lubricating oil thrown towards the cylinder head 12 can be further strengthened, reducing the possibility that the oil discharge volume will increase with the increase of the operating frequency under high frequency conditions. This makes it easier to take into account the performance of the reciprocating compressor 100 under different high frequency conditions.

[0058] As an example, the oil baffle 4 can be fixedly connected to the crankshaft connection 31 so that the oil baffle 4 moves with the crankshaft connection 31; or, 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 section 22 and the crankshaft connection 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 covers the eccentric shaft section 22 and the crankshaft connection 31, the connecting rod 3 passes through the first opening 41b, the first opening 41d is opposite to the piston 5, and the second opening 41e is opposite to the corresponding cylinder wall of the cylinder chamber 12a.

[0059] Furthermore, since the first opening 41d is opposite to the piston 5 and is connected to the first opening 41b, it facilitates further reduction of the risk of interference between the connecting rod 3 and the oil baffle 4. 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, the oil baffle 4 is fixedly connected to the crankcase 1), the first opening 41d and the first opening 41b can provide some clearance to 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 connecting part 31, the distance between the oil baffle 4 and the piston 5 remains basically constant, and the dimensions of the first opening 41d and the first opening 41b do not need to consider clearance from the piston 5. The first opening 41d can still achieve lubrication of the piston 5 and the cylinder head 12.

[0060] As an example, the bottom of the piston compressor 100 has an oil sump, and an oil guide groove 211 is formed on the main shaft section 21. The oil guide groove 211 can be provided on the outer peripheral wall of the main shaft section 21 and extend spirally along the axial direction of the main shaft section 21. The oil guide groove 211 is connected to the oil sling hole 22a. For example, the oil guide groove 211 and the oil sling hole 22a are connected inside the crankshaft 2. When the crankshaft 2 rotates, the centrifugal force generated by the oil guide groove 211 of the main shaft section 21 draws the lubricating oil at the bottom upward, and then pumps the lubricating oil to the oil sling hole 22a of the eccentric shaft section 22 through the oil guide groove 211 of the main shaft section 21. Under the action of the centrifugal force generated by the rotation of the crankshaft 2, the lubricating oil in the oil sling hole 22a is thrown out of the eccentric shaft section 22 and thrown to the surroundings.

[0061] For example, the width of the second opening 41c in the circumferential direction of the crankshaft 2 decreases linearly or non-linearly (e.g., in a stepwise manner) away from the first opening 41b.

[0062] It is understood that the reciprocating compressor 100 also includes a housing 10, within which the crankcase 1, crankshaft 2, connecting rod 3, and oil baffle 4 are all housed. The housing 10 serves as an external protective cover for the reciprocating compressor 100, providing not only mechanical support but also a sealing function to prevent external impurities from entering the interior of the reciprocating compressor 100. The reciprocating compressor 100 also includes a drive structure (not shown in the figure), which is located within the housing 10 and connected to the main shaft section 21, enabling the drive structure to drive the crankshaft 2 to rotate. The central axis of the main shaft section 21 serves as the rotation axis of the crankshaft 2. The central axis of the eccentric shaft section 22 is parallel and spaced apart from the central axis of the main shaft section 21. Under the drive of the drive structure, the eccentric shaft section 22 rotates eccentrically, thereby driving the piston 5 to reciprocate via the connecting rod 3. Taking a drive structure including a drive motor as an example, 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, while the rotor is connected to the crankshaft 2 to achieve the rotation of the crankshaft 2.

[0063] According to an embodiment of the present invention, the piston compressor 100 is provided with an oil baffle 4 covering the eccentric shaft section 22 and the crankshaft connection portion 31, with the first opening 41d facing the piston 5 and the second opening 41e facing the corresponding cylinder wall of the cylinder chamber 12a. The circumferential width of the second opening 41e decreases in the direction away from the first opening 41b, and the maximum circumferential width of the second opening 41e is less than or equal to the minimum circumferential width of the first opening 41d. This makes it less likely that the oil baffle 4 will restrict the amount of oil supplied under low-frequency operating conditions. At the same time, the oil baffle 4 can restrict the amount of oil supplied under high-frequency operating conditions, improve the problem of high oil discharge at high frequencies, and thus improve the performance of the piston compressor 100. Moreover, regardless of whether it is high-frequency or low-frequency operation, the oil baffle 4 can direct the lubricating oil towards the piston 5 and the cylinder head 12, achieving reliable lubrication of the piston 5 and the cylinder head 12. It is less likely that the amount of lubricating oil directed towards the piston 5 and the cylinder head 12 will be excessively restricted by the oil baffle 4 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 crankshaft connection 31 without adjusting other components of the piston compressor 100, which helps to reduce design costs.

[0064] Optionally, such as Figure 1 , Figure 2 , Figure 4 As shown, the two ends of the second opening 41e in the axial direction of the crankshaft 2 are flush with the inner and outer wall surfaces of the corresponding cylinder walls, respectively. For example, if the axial direction of the crankshaft 2 is vertical, the upper edge of the second opening 41e is flush with the outer wall surface 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 surface of the upper cylinder wall 12b of the cylinder cavity 12a. Of course, in other embodiments, the upper edge of the second opening 41e may also be located above the outer wall surface of the upper cylinder wall 12b of the cylinder cavity 12a.

[0065] It is understandable that the second opening 41e can penetrate the upper end of the peripheral wall 41 of the oil baffle 4, or, as... Figure 2 , Figure 4 and Figure 7 As shown, the second opening 41e is spaced apart from the upper end of the peripheral wall 41 of the oil baffle 4.

[0066] In some embodiments, such as Figure 7 As shown, at least one of the two circumferential edges of the second opening 41e extends spirally along the axial direction of the oil baffle 4, so the second opening 41e is roughly formed as a trapezoidal opening or a triangular opening. The structure of the second opening 41e is simple and easy to process.

[0067] 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.

[0068] For example, such as Figure 7 As shown, the two circumferential edges of the second opening 41e extend spirally along the axial direction of the oil baffle 4, and the spiral directions of the two circumferential edges of the second opening 41e are opposite, with their spiral angles being approximately equal. This makes the second opening 41e roughly form an isosceles trapezoid or isosceles triangle, giving it a certain degree of symmetry. This facilitates better alignment between the second opening 41e and the corresponding cylinder wall of the cylinder cavity 12a, enabling lubrication of the piston 5 and cylinder head 12 with a smaller amount of oil under high-frequency operating conditions. Of course, the spiral directions of the two circumferential edges of the second opening 41e can also be the same, and / or the spiral angles of the two circumferential edges of the second opening 41e can be unequal; or, one of the two circumferential edges of the second opening 41e can extend spirally, while the other extends linearly along the axial direction of the oil baffle 4.

[0069] In some embodiments, such as Figure 7 and Figure 8 As shown, the circumferential width t1 of the first opening 41d remains constant or decreases in the direction away from the first opening 41b, facilitating the processing of the first opening 41d. Wherein, the minimum circumferential width of the first opening 41d is greater than the maximum circumferential width of the second opening 41e, resulting in an abrupt change in circumferential width at the junction of the first opening 41d and the second opening 41e. This creates a significant difference in circumferential width between the two openings, ensuring that under low-frequency operation of the reciprocating compressor 100, the first opening 41d provides sufficient flow space for lubricating oil to be ejected, while under high-frequency operation, the second opening 41e reliably blocks the lubricating oil, limiting its ejection towards the cylinder head. The lubricating oil volume of 12; and / or, the maximum circumferential width of the first opening 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 the avoidance of the connecting rod 3. At the same time, under the low-frequency operation of the piston compressor 100, even if some lubricating oil is thrown out through the first opening 41b, the first opening 41b can provide sufficient flow space for it, so as to further weaken the obstruction of the oil baffle 4 to the lubricating oil thrown towards the piston 5 and cylinder head 12 under the low-frequency operation, and achieve reliable lubrication of the piston 5 and cylinder head 12.

[0070] For example, such as 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 adapting to the changing trend of the circumferential width between the first opening 41b and the second opening 41e. Furthermore, the changing trend of the circumferential width of the first opening 41d is consistent with the changing trend of the circumferential width of the second opening 41e, which facilitates processing. The circumferential width of the first opening 41b can remain constant along the axial direction, but is not limited to this. For example, the circumferential width of the first opening 41b can decrease towards 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 opening 41d can remain unchanged along the axial direction. In this case, the circumferential width of the first opening 41b can remain unchanged along the axial direction or decrease towards the second opening 41c.

[0071] Optionally, at least one of the two circumferential ends of the first opening 41d extends spirally along the axial direction of the oil baffle 4, so that the circumferential width of the first opening 41d decreases in the direction away from the first opening 41b.

[0072] In some embodiments, such 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. Exemplarily, the first opening 41b penetrates the lower end of the peripheral wall 41 of the oil baffle 4, facilitating a smoother installation of the peripheral wall 41 of the oil baffle 4 over the eccentric shaft section 22 and the crankshaft connection portion 31, thus facilitating the assembly of the piston compressor 100. For example, the connecting rod 3 and the eccentric shaft section 22 can be assembled first, and then the oil baffle 4 can be axially installed over the eccentric shaft section 22 and the crankshaft connection 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 inserted through the first opening 41b first, and assembly with the eccentric shaft section 22 can be achieved within the oil baffle 4.

[0073] In some embodiments, such as Figures 2-5As shown, a through clearance notch 12c is formed on the cylinder wall of cylinder chamber 12a on the side away from the first through hole 11d in the axial direction of crankshaft 2. The clearance notch 12c penetrates the cylinder wall of cylinder chamber 12a at the end facing the second opening 41c, so that the clearance notch 12c is opposite to the second opening 41e. A part of piston 5 is adapted to be exposed through the clearance notch 12c. Thus, a part of the lubricating oil thrown out through opening 41a can fall into the clearance notch 12c and flow to the surface of piston 5 during piston 5 movement to lubricate the friction pair between piston 5 and cylinder head 12. This facilitates reliable lubrication with a small amount of oil, especially under high-frequency operating conditions, where the flow space provided by the oil baffle 4 for lubricating oil is relatively small. Since the second opening 41e is opposite to the clearance notch 12c, more lubricating oil thrown out from the second opening 41e can be thrown into the clearance notch 12c. This achieves reliable lubrication of piston 5 and cylinder head 12 while limiting the amount of oil thrown out.

[0074] For example, such as Figures 2-5 As shown, a clearance notch 12c is formed in the upper cavity wall of the cylinder chamber 12a. The clearance notch 12c penetrates the upper cavity wall along its thickness direction and also penetrates the end of the upper cylinder wall 12b facing the second opening 41c to form a groove, so that the groove of the clearance notch 12c is opposite to the second opening 41e. The piston 5 reciprocates within 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 in a position near the bottom dead center, a portion of the piston 5 can be exposed through the clearance notch 12c, for example, in conjunction with... Figure 2 and Figure 5 The piston 5 is connected to the piston connection 32 by a piston pin 51. The piston 5 is located on the piston pin 51 facing the oil baffle 4 and the piston pin 51 is adapted to be exposed through the clearance notch 12c.

[0075] Optionally, such as Figures 2-5 and Figure 7 As shown, the maximum circumferential width of the second opening 41e is 0.9 to 1.1 times the groove width t3 of the relief notch 12c. For example, the circumferential width of the lower end of the second opening 41e is 0.9 to 1.1 times the groove width t3 of the relief notch 12c. Therefore, the relative size of the second opening 41e and the relief notch 12c is more suitable, so that under high-frequency operating conditions, the oil baffle 4 can better block the lubricating oil thrown from the oil throwing hole 22a to the gas position other than the relief notch 12c. It is not easy for the oil baffle 4 to weaken its oil-blocking effect or the directional oil throwing effect if the second opening 41e is too large, nor is it easy for the amount of oil thrown to the relief notch 12c to be too small if the second opening 41e is too small, which would limit the lubrication effect.

[0076] In some embodiments, such as Figure 5 and Figure 6As shown, the main body 11 has 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 through a connecting channel 11e. One axial end of the second exhaust chamber 11b is connected to an inner exhaust pipe 9, and 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 position where the second exhaust chamber 11b is connected to the connecting channel 11e is far away from the position where the second exhaust chamber 11b is connected to the inner exhaust pipe 9. At the same time, the gas flowing from the connecting channel 11e to the second exhaust chamber 11b flows away from the inner exhaust pipe 9 into the second exhaust chamber 11b, which facilitates better collection and buffering of high-pressure gas in the second exhaust chamber 11b and reduces airflow pulsation.

[0077] For example, such as 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 helps to appropriately enhance the throttling effect of the connecting channel 11e on the high-pressure airflow inside, so as to further reduce the pulsation in the airflow and reduce the noise generated by the pulsation.

[0078] In some embodiments, such as Figure 3 and Figure 7 As shown, the peripheral wall 41 of the oil baffle 4 is open at the end facing the crankcase 1. 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 helps to improve the structural strength of the oil baffle 4. The end wall 42 closes a portion of 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 portion of the upper end of the peripheral wall 41. Then, a third opening 42a is formed on the end wall 42. Part of the lubricating oil thrown out from the oil throwing hole 22a can be thrown through the third opening 42a to the inner wall of the housing 10 of the piston compressor 100 to contact and dissipate heat from the housing 10.

[0079] In some embodiments, such as Figure 2 and Figure 10 As shown, the outer peripheral wall of the eccentric shaft section 22 includes a first wall portion 221 and a second wall portion 222. The first wall portion 221 mates with the crankshaft connecting portion 31. The second wall portion 222 is located on the side of the first wall portion 221 away from the main shaft section 21, and the second wall portion 222 is opposite to the first opening 41d. The oil slinger hole 22a penetrates 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 41d, which facilitates the better orientation of the oil slinged out from the first oil outlet 22b toward the first opening 41d; and / or, as Figure 2 , Figure 10 and Figure 11As shown, the end of the eccentric shaft section 22 away from the main shaft section 21 does not extend beyond the cylinder wall of the cylinder chamber 12a away from the perforation. The oil slinger hole 22a penetrates the end face of the eccentric shaft section 22 away from the main shaft section 21 to form the second oil outlet 22c. The crankshaft connection part 31 does not block the second oil outlet 22c, so that the lubricating oil can be thrown out from the second oil outlet 22c to the surrounding area, so that some of the lubricating oil is thrown towards the piston 5 and the cylinder head 12.

[0080] For example, the oil slinger hole 22a penetrates the upper end face of the eccentric shaft section 22. The upper end face of the eccentric shaft section 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 vertical direction (including the upper end face of the eccentric shaft section 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 section 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 vertical direction.

[0081] In some embodiments, such as Figure 3 , Figure 5 and Figure 6 As shown, the oil baffle 4 is fixed to the crankcase 1. It can be understood that the oil baffle 4 can be directly fixed to the crankcase 1, or the oil baffle 4 can be indirectly fixed to the crankcase 1 through other components. It is only necessary to keep the oil baffle 4 stationary relative to the crankcase 1. At this time, the eccentric shaft section 22 and the crankshaft connecting part 31 can move relative to the oil baffle 4 within the oil baffle 4.

[0082] Therefore, since the oil baffle 4 is not fixed to the crankshaft 2 and connecting rod 3, and does not move with the crankshaft 2 and connecting rod 3, the original dynamic balance setting of the reciprocating compressor 100 without the oil baffle 4 is not likely to require a redesign of the dynamic platform due to the addition of the oil baffle 4, which helps to reduce design costs. In other words, the dynamic balance design of the reciprocating 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 by the drive structure connected to the crankshaft 2, so the addition of the oil baffle 4 will not increase the load on the drive structure and will not place higher requirements on the drive structure. Moreover, since the oil baffle 4 does not move relative to the cylinder head 12, the relative position of the oil baffle 4 and the cylinder head 12 is... The fact that the position remains unchanged is beneficial for improving the directional oil throwing effect of the oil thrown towards the piston 5 and cylinder head 12 through the second opening 41c. It is less likely that the relative position between the second opening and the cylinder head 12 will change due to the movement of the oil baffle 4, which would impose too many restrictions on the directional oil throwing effect. In addition, it is easier to place the oil baffle 4 closer to the cylinder head 12 within the allowable arrangement space. This helps to reduce the distance between the first opening 41d and the piston 5, and the distance between the second opening 41e and the cylinder head 12. This makes it easier for the lubricating oil thrown from the opening 41a to lubricate the piston 5 and cylinder head 12 more promptly and in a more directional manner, which helps to improve the directional oil throwing effect on the cylinder head 12 and piston 5.

[0083] Optionally, such 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 beneficial to improving the directional oil throwing effect, and the oil baffle 4 will not affect the reciprocating motion of the piston 5.

[0084] For example, such as Figure 2 As shown, piston 5 reciprocates within cylinder chamber 12a between top dead center and bottom dead center. When piston 5 is at bottom dead center, or when piston 5 is in a position near bottom dead center, piston 5 can pass through the second opening 41c. Piston 5 moves toward top dead center and can disengage from the second opening 41c.

[0085] In some embodiments, such as Figure 3 , Figure 5 and Figure 6 As shown, at least one exhaust chamber 11c is formed on the main body 11. The exhaust chamber 11c is located on the outer periphery of the first through hole 11d, and the exhaust chamber 11c is directly or indirectly connected to the exhaust port 12d of the cylinder chamber 12a. For example, there may be one exhaust chamber 11c, which is directly or indirectly connected to the exhaust port 12d of the cylinder chamber 12a; or there may be multiple exhaust chambers 11c, where one exhaust chamber 11c located adjacent to the cylinder chamber 12a is directly or indirectly connected to the exhaust port 12d of the cylinder chamber 12a, and the remaining cylinder chambers 12a can be indirectly connected to the exhaust port 12d of the cylinder chamber 12a through the aforementioned exhaust chamber 11c. Adjacent exhaust chambers 11c may be connected. Therefore, the exhaust chamber 11c is connected between the 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. It can collect and buffer the high-pressure pulsating gas discharged from the cylinder chamber 12a. When the pulsating airflow enters the larger space of the exhaust chamber 11c, the airflow speed is reduced and the pressure fluctuation is weakened, thereby reducing the impact on the subsequent pipeline system and helping to reduce vibration and noise.

[0086] The oil baffle 4 has a connecting arm 43 on its peripheral wall 41. The connecting arm 43 is fixedly connected to the cavity wall of the exhaust chamber 11c. This allows the oil baffle 4 to be fixedly installed while not affecting the flow path of the gas in the piston compressor 100. It also makes it easier to simplify the structure of the crankcase 1 without having to separately process a fixing structure for fixing the oil baffle 4.

[0087] For example, in Figure 3 , Figure 5 and Figure 7In the example, the connecting arm 43 extends in a straight line, with one end integrally connected to the peripheral wall 41 of the oil baffle 4, and the other end connected to the cavity wall of the exhaust chamber 11c. Of course, the structural form of the connecting arm 43 is not limited to this.

[0088] In some embodiments, such as Figures 2-4 and Figure 6 As shown, the peripheral wall 41 of the oil baffle 4 abuts against the crankcase 1. One end of the exhaust chamber 11c is open and the long end of the exhaust chamber 11c is provided with a chamber cover 6. Fasteners 7 (such as screws) are threaded through the chamber cover 6. The fasteners 7 are threadedly connected to the crankcase 1 so that the chamber cover 6 is sealed at the open end of the exhaust chamber 11c. A second through hole 6a is formed on the chamber cover 6 for the fasteners 7 to pass through. Under the fastening action of the fasteners 7, the exhaust chamber 11c is sealed. The assembly is simple. Moreover, the above-mentioned arrangement of the exhaust chamber 11c facilitates the processing of the crankcase 1. For example, if the crankcase 1 is a one-piece molded part, the open arrangement of one end of the exhaust chamber 11c facilitates the processing feasibility of the crankcase 1.

[0089] In this design, fastener 7 passes through connecting arm 43, which is sandwiched between fastener 7 and cavity cover 6. Connecting arm 43 has a third through hole 43a for fastener 7 to pass through. Under the tightening action of fastener 7, the portion surrounding the edge of the third through hole 43a is sandwiched between fastener 7 and cavity cover 6, thus fixing oil baffle 4. Simultaneously, since the peripheral wall 41 of oil baffle 4 abuts against crankcase 1, the portion surrounding the edge of the third through hole 43a can provide a certain degree of compression and sealing to the gap between fastener 7 and second through hole 6a, facilitating improved sealing between fastener 7 and cavity cover 6. It can be understood that fastener 7 can both seal the cavity cover 6 against the exhaust chamber 11c and install oil baffle 4, and the installation of oil baffle 4 is unlikely to excessively affect the sealing of exhaust chamber 11c, achieving "multi-purpose functionality." The piston compressor 100 has a simple structure and low cost.

[0090] 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: sealing is achieved by compression between the wall of the second through hole 6a and the fastener 7; a sealing element is provided between the fastener 7 and the cavity cover 6; a sealing gasket 8 is added between the connecting arm 43 and the cavity cover 6; and sealing gaskets 8 are added to both sides of the connecting arm 43 along the length of the fastener 7. Optionally, the sealing gasket 8 is a metal part.

[0091] It is understandable that when there are multiple exhaust chambers 11c, if there is only one connecting arm 43, the connecting arm 43 can be connected to the cavity wall of any exhaust chamber 11c; or, if there are multiple connecting arms 43, each connecting arm 43 is connected to the cavity wall of the corresponding exhaust chamber 11c.

[0092] In some embodiments, such as Figure 3 , Figure 4 and Figure 7 As shown, the peripheral wall 41 of the oil baffle 4 is arranged around the portion of the crankshaft 2 extending out of the first through hole 11d, and the oil baffle 4 is positioned adjacent to the exhaust chamber 11c. The peripheral wall 41 of the oil baffle 4 forms a clearance opening 41f spaced apart from the opening 41a. The clearance opening 41f avoids the position of the crankcase 1 corresponding to the exhaust chamber 11c. Thus, the clearance opening 41f avoids the portion of the cavity wall of the exhaust chamber 11c defined by the crankcase 1. If one end of the exhaust chamber 11c is open and covered with a cavity cover 6, the clearance opening 41f can also avoid the cavity cover 6. Therefore, the oil baffle 4 can be arranged to avoid the exhaust chamber 11c, making it easier for the oil baffle 4 to be positioned closer to the cylinder head 12. At the same time, the cavity wall of the exhaust chamber 11c can block the clearance opening 41f to a certain extent, reducing the amount of oil thrown out from the clearance opening 41f and improving the problem of lubricating oil splashing. The shape of the clearance opening 41f can be adjusted according to the required clearance structure.

[0093] It is understood that the clearance port 41f can accommodate at least one exhaust chamber 11c. For example, as... Figure 3 , Figure 4 and Figure 7 As shown, there are multiple exhaust chambers 11c, and the avoidance port 41f avoids all exhaust chambers 11c. The multiple exhaust chambers 11c are connected in series. The gas that has been compressed in the cylinder chamber 12a flows through the multiple exhaust chambers 11c in sequence through the exhaust port 12d. The multiple exhaust chambers 11c can form a multi-stage buffer, making the pressure of the discharged gas more stable. If the exhaust chamber 11c is connected to the inner exhaust pipe 9, the inner exhaust pipe 9 can be connected to the exhaust pipe of the piston compressor 100. The clearance port 41f can be reasonably set according to the arrangement requirements of the inner exhaust pipe 9 so that the clearance port 41f can also avoid the inner exhaust pipe 9. In the example in the figure, the second exhaust chamber 11b is connected to the inner exhaust pipe 9. A part of the inner exhaust pipe 9 bends and extends toward the oil baffle 4. The clearance port 41f avoids 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 surrounds the crankcase 1 so that the inner exhaust pipe 9 is far away from the oil baffle 4, then the clearance port 41f does not need to avoid the inner exhaust pipe 9.

[0094] For example, such as 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 through the first through hole 11d. If a balance 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 balance block 23.

[0095] In some embodiments, such as Figure 4 and Figure 7As shown, both the opening 41a and the clearance opening 41f penetrate one end of the peripheral wall 41 of the oil baffle 4 adjacent to the first through hole 11d, facilitating the installation of the oil baffle 4. For example, the oil baffle 4 can approach the crankcase 1 along the axial direction of the crankshaft 2 until it reaches a predetermined position (e.g., the oil baffle 4 abuts against the crankcase 1, and / or, the connecting arm 43 abuts against the cavity cover 6). The peripheral wall 41 of the oil baffle 4 has a first portion 411 and a second portion 412 spaced apart circumferentially. The first portion 411 is located between the opening 41a and the clearance opening 41f and is in communication with the cylinder cavity 12a and the exhaust cavity 11c. Relatively speaking, the circumferential width of the first part 411 is smaller than the circumferential width of the first opening 41b, and the circumferential width of the first part 411 is smaller than the circumferential width of the clearance opening 41f. The second part 412 is located between the opening 41a and the clearance opening 41f, and the second part 412 is set away from the communication position between the cylinder chamber 12a and the exhaust chamber 11c. The circumferential width of the second part 412 is larger than the circumferential width of the first opening 41b, and the circumferential width of the second part 412 is larger than the circumferential width of the clearance opening 41f. The first part 411 is spaced apart from the crankcase 1, and the second part 412 abuts against the crankcase 1.

[0096] Therefore, since the second part 412 abuts against the crankcase 1, and with the setting of the connecting arm 43, the oil baffle 4 can be reliably fixed. Moreover, the circumferential width of the second part 412 is relatively large, while the circumferential width of the first part 411 is relatively small, which can ensure that the oil baffle 4 abuts against the crankcase 1 and prevent the second part 412 from being crushed. At the same time, compared with the second part 412, the first part 411 is set closer to the connecting arm 43, and the first part 411 does not abut against the crankcase 1, which can improve the problem that the first part 411 is easily crushed, which is conducive to balancing the reliability of the oil baffle 4 and the installation firmness.

[0097] In some embodiments, such as Figures 1-3 As shown, the peripheral wall 41 of the oil baffle 4 is open at the end facing the crankcase 1. 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. The end wall 42 has a third opening 42a, which extends through the end wall 42 along the thickness direction. Part of the lubricating oil thrown out from the oil throwing hole 22a can be thrown through the third opening 42a to the inner wall of the housing 10 of the piston compressor 100 to contact and dissipate heat from the housing 10.

[0098] In the cross-section of crankshaft 2, the orthographic projection of the peripheral wall 41 of the third opening 42a is located outside the movement trajectory of the oil outlet of the oil slinger 22a. The oil outlet of the oil slinger 22a can be understood as the oil outlet being formed on the outer surface of the eccentric shaft section 22. Therefore, in the cross-section of crankshaft 2, the orthographic projection of the peripheral wall 41 of the third opening 42a is located outside the orthographic projection of the movement trajectory of the oil outlet. Thus, regardless of where the oil outlet of the oil slinger 22a moves with the eccentric shaft section 22, it facilitates the smooth and direct flow of the ejected lubricating oil through the third opening 42a towards the housing 10, which is beneficial for continuous heat dissipation from the housing 10.

[0099] It is understandable that the shape of the third opening 42a is not restricted. For example, the third opening 42a can be a circular opening, a polygonal opening (such as a square opening), etc.

[0100] 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. The end wall 42 is formed into an annular structure so that the end wall 42 defines the 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.

[0101] In some embodiments, such as Figure 1 and Figure 2 As shown, the crankshaft 2 also includes a balance block 23, which is connected between the main shaft section 21 and the eccentric shaft section 22, and / or, the balance block 23 is 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 covered outside the balance block 23. Therefore, the oil baffle 4 is less likely to interfere with the balance block 23, and the oil baffle 4 can be set closer to the cylinder head 12 and the piston 5, which is beneficial to improving the directional oil throwing effect.

[0102] It is understandable that when the end of the eccentric shaft section 22 away from the main shaft section 21 is connected to the balance block 23, the balance block 23 also avoids the oil outlet position of the oil slinger hole 22a. For example, the balance block 23 is sleeved outside the eccentric shaft section 22, and the oil slinger hole 22a penetrates the end face of the eccentric shaft section 22 away from the main shaft section 21 to form the second oil outlet 22c.

[0103] In some embodiments, the piston compressor 100 further includes a muffler connected upstream of the air inlet of the cylinder chamber 12a. The airflow first flows through the muffler and then flows to the cylinder chamber 12a. In the direction of piston 5 movement, the muffler is located on the side of the cylinder head 12 away from the oil baffle 4. In the circumferential direction of the crankshaft 2, the muffler is located on the lower side of the cylinder head 12. The arrangement of the oil baffle 4 helps to reduce the amount of oil flowing into the muffler.

[0104] The inventors of this application conducted high-frequency and low-frequency operating condition tests on multiple sets of comparative examples and multiple sets of embodiments of this application. The test results are shown in Tables 1-2 below. The test methods are well known to those skilled in the art. Comparative examples 1-9 did not use oil baffles. Embodiments 1-9 added oil baffles 4 to the comparative examples 1-9. Other conditions were the same, and the average oil discharge was the average of the maximum values ​​of the three time periods.

[0105] As can be clearly seen from Table 1, under the high-frequency operating condition of 75Hz, the average oil discharge per hour of the comparative 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 comparative example, representing a decrease of approximately 58.4%. As can be clearly seen from Table 2, under the high-frequency operating condition of 75Hz, the embodiment shows a 3.7W increase in cooling capacity, a 0.003 increase in COP, and a 0.3dB reduction in operating noise compared to the comparative example. Under the low-frequency operating condition of 27Hz, the embodiment shows a 1.1W increase in cooling capacity, a 0.018 increase in COP, and a 0.36dB reduction in operating noise compared to the comparative example. Therefore, the oil baffle 4 in the embodiment of this application not only improves the problem of excessive oil discharge at high frequencies but also enhances cooling capacity and reduces operating noise to a certain extent.

[0106] Table 1. Comparison of oil output test results between the comparative example and the embodiment under high-frequency operating conditions.

[0107]

[0108] Table 2 Comparison of performance test results of comparative examples and embodiments under high-frequency and low-frequency operating conditions.

[0109]

[0110] According to a second aspect embodiment of the refrigeration device 200, such as Figure 12 As shown, the device includes a reciprocating compressor 100 according to the first aspect embodiment of the present invention. The reciprocating compressor 100 is used in the refrigerant circulation system of the refrigeration equipment 200 to provide power for the refrigeration cycle.

[0111] According to the refrigeration equipment 200 of the present invention, by employing the above-described piston compressor 100, the refrigeration performance of the refrigeration equipment 200 is improved.

[0112] It is worth noting that the type of refrigeration equipment 200 according to the embodiments of this application is not limited. For example, the refrigeration equipment 200 can be a refrigerator, freezer, freezer, cold storage, or ice maker, etc.

[0113] Other configurations and operations of the refrigeration device 200 according to embodiments of the present invention are known to those skilled in the art and will not be described in detail here.

[0114] Furthermore, it should be noted that the various specific technical features described in the above specific embodiments can be combined in any suitable manner without contradiction. To avoid unnecessary repetition, this application will not describe the various possible combinations separately. In addition, various different embodiments of this application can also be arbitrarily combined, as long as they do not violate the spirit of this application, they should also be regarded as the content disclosed in this application.

[0115] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0116] 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.

[0117] 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.

[0118] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which 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 having a first through hole, and the cylinder head having a cylinder chamber; A crankshaft, comprising a main shaft section and an eccentric shaft section, the main shaft section being rotatably fitted into the first through hole, and the eccentric shaft section having an oil slinger hole extending through its outer surface; The connecting rod has a crankshaft connecting part and a piston connecting part at both ends. The crankshaft connecting part is sleeved outside the eccentric shaft section and is arranged to avoid the oil slinger hole. The piston connecting part is connected to the piston located in the cylinder chamber. An oil baffle is provided, which covers the eccentric shaft section and the crankshaft connection. The peripheral wall of the oil baffle has an opening opposite to one end of the cylinder head in the piston movement direction. The opening includes a first opening and a second opening. The connecting rod passes through the first opening. The second opening is connected to the end of the first opening in the crankshaft axial direction away from the first through hole, and includes a first opening and a second opening connected in the crankshaft axial direction. The first opening is opposite to the piston, and the second opening is opposite to the cylinder wall of the cylinder chamber in the crankshaft axial direction away from the first through hole. The circumferential width of the second opening decreases in the direction away from the first opening, and the maximum circumferential width of the second opening is less than or equal to the minimum circumferential width of the first opening.

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

3. The reciprocating compressor according to claim 1, characterized in that, The circumferential width of the first opening remains unchanged or decreases in the 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 opening is less than or equal to the circumferential width of the first opening.

4. The reciprocating compressor according to claim 1, characterized in that, The cylinder cavity has a through-hole relief notch formed on the side of the cylinder wall away from the first perforation in the axial direction of the crankshaft. The relief notch penetrates the end of the cylinder wall facing the second opening, so that the relief notch is opposite to the second opening. A portion of the piston is adapted to be exposed through the relief notch. The maximum circumferential width of the second opening is 0.9 to 1.1 times the width of the notch.

5. The reciprocating compressor according to claim 1, characterized in that, The main body has a first exhaust chamber and a second exhaust chamber. The first exhaust chamber is connected to the exhaust port of the cylinder chamber, and the second exhaust chamber is connected to the first exhaust chamber through a connecting channel. An inner exhaust pipe is connected to one axial end of the second exhaust chamber. The connecting channel extends obliquely from the first exhaust chamber toward the second exhaust chamber toward the other end of the axial direction of the second exhaust chamber.

6. The reciprocating compressor according to claim 1, characterized in that, The peripheral wall of the oil baffle is open at one end facing the crankcase. The oil baffle also has an end wall connected to the end of the peripheral wall of the oil baffle away from the crankcase, and the end wall closes the corresponding end portion of the peripheral wall.

7. The reciprocating compressor according to claim 1, characterized in that, The outer peripheral wall of the eccentric shaft section includes a first wall portion and a second wall portion. The first wall portion mates with the crankshaft connecting portion. The second wall portion is located on the side of the first wall portion away from the main shaft section and is opposite to the first opening. The oil slinger hole penetrates the second wall portion to form a first oil outlet, which is opposite to the first opening; and / or, The end of the eccentric shaft segment away from the main shaft segment does not extend beyond the cylinder wall of the cylinder cavity away from the perforation, and the oil slinger hole penetrates the end face of the eccentric shaft segment away from the main shaft segment to form a second oil outlet.

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

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

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

11. The reciprocating compressor according to claim 10, characterized in that, The peripheral wall of the oil baffle abuts against the crankcase. One end of the exhaust chamber is open and has a chamber cover. A fastener passes through the chamber cover and is threadedly connected to the crankcase, so that the chamber cover seals the open end of the exhaust chamber. The fastener passes through the connecting arm, and the connecting arm is sandwiched between the fastener and the cavity cover.

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

13. The reciprocating compressor according to claim 12, characterized in that, Both the opening and the clearance opening penetrate through one end of the peripheral wall of the oil baffle adjacent to the first through hole. The oil baffle has a first portion and a second portion spaced apart circumferentially. The first portion is located between the opening and the clearance opening and is opposite to the communication position between the cylinder chamber and the exhaust chamber. The circumferential width of the first portion is smaller than the circumferential width of the first opening and smaller than the circumferential width of the clearance opening. The second portion is located between the opening and the clearance opening and is disposed away from the communication position between the cylinder chamber and the exhaust chamber. The circumferential width of the second portion is larger than the circumferential width of the first opening and larger than the circumferential width of the clearance opening. The first portion is spaced apart from the crankcase, and the second portion abuts against the crankcase.

14. The reciprocating compressor according to claim 8, characterized in that, The peripheral wall of the oil baffle is open at one end facing the crankcase. The oil baffle also has an end wall connected to the end of the peripheral wall of the oil baffle away from the crankcase. The end wall forms a third opening. 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 slinger.

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

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

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