Compressor piston, pump body assembly and compressor

Abstract

The utility model discloses a compressor piston, a pump body assembly and a compressor. The compressor piston comprises a piston body. Specifically, a mounting hole is formed in the piston body, the mounting hole is provided with a first hole section and second hole sections located at the two ends of the first hole section, the second hole sections and the first hole section are coaxially arranged, the outer diameter of each second hole section is larger than that of the first hole section, a sinking groove is formed in the inner wall face of each second hole section, and a chamfer is arranged at the end, away from the first hole section, of each second hole section. The double-rotor compressor can solve the problem that a piston of a double-rotor compressor in the prior art is difficult to adapt to the shortened middle shaft section.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to a compressor piston, a pump body assembly and a compressor. BACKGROUND

[0002] A double-rotor compressor includes a cylinder, a crankshaft and two pistons, wherein the crankshaft has two eccentric portions, and each eccentric portion is sleeved with a piston. When the crankshaft rotates, the two eccentric portions of the crankshaft rotate together and drive the two pistons to rotate synchronously, thereby compressing the gas.

[0003] At present, in order to improve the vibration and noise of the compressor, the intermediate shaft section between the two eccentric portions of the crankshaft is usually shortened. However, the existing piston is difficult to adapt to the shortened intermediate shaft section, thereby being difficult to improve the vibration and noise of the compressor. CONTENT OF THE UTILITY MODEL

[0004] The main purpose of the present application is to provide a compressor piston, a pump body assembly and a compressor to solve the problem that the piston of the double-rotor compressor in the prior art is difficult to adapt to the shortened intermediate shaft section.

[0005] According to one aspect of the present application, a compressor piston is provided, comprising:

[0006] A piston body is provided with a mounting hole, the mounting hole has a first hole section and a second hole section located at both ends of the first hole section, the second hole section is coaxially arranged with the first hole section, the outer diameter of the second hole section is greater than that of the first hole section, the inner wall surface of the second hole section is provided with a groove, and the end of the second hole section away from the first hole section is provided with a chamfer.

[0007] Further, along the axial direction of the mounting hole, the distance between the second hole section and the end surface of the piston body is h;

[0008] Along the radial direction of the mounting hole, the distance between the vertex of the outer wall surface of the chamfer and the outer wall surface of the first hole section is c;

[0009] Wherein, h and c satisfy the relationship: h > c.

[0010] Further, along the axial direction of the mounting hole, the height of the piston body is HP;

[0011] Along the axial direction of the mounting hole, the distance between the second hole section and the end surface of the piston body is h;

[0012] Wherein, HP and h satisfy the relationship: h / HP, and 0.275≤h / HP≤0.437.

[0013] Further, the inner wall surface of the second hole section and the outer wall surface of the first hole section form the sink groove, and along the radial direction of the mounting hole, the depth of the sink groove is d;

[0014] Along the radial direction of the mounting hole, the distance between the outer wall surface of the piston body and the outer wall surface of the first hole section is TP;

[0015] Along the radial direction of the mounting hole, the distance between the vertex of the outer wall surface of the chamfer and the outer wall surface of the first hole section is c;

[0016] Wherein, d, c and TP satisfy the relationship: (c+d) / TP, and 0.22≤(c+d) / TP≤0.5.

[0017] Further, along the radial direction of the mounting hole, the distance c between the vertex of the outer wall surface of the chamfer and the outer wall surface of the first hole section satisfies the relationship: c≥0.5mm; and / or,

[0018] Along the axial direction of the mounting hole, the distance h between the second hole section and the end surface of the piston body satisfies the relationship: 2.5mm≤h≤3.5mm; and / or,

[0019] Along the radial direction of the mounting hole, the depth d of the sink groove satisfies the relationship: 0.7mm≤d≤1mm; and / or,

[0020] Along the axial direction of the mounting hole, the height HP of the piston body satisfies the relationship: 15mm≤HP≤22mm; and / or,

[0021] Along the radial direction of the mounting hole, the distance TP between the outer wall surface of the piston body and the outer wall surface of the first hole section satisfies the relationship: 5.5mm≤TP≤7.5mm.

[0022] Further, the degree r of the chamfer satisfies the relationship: r≤20°.

[0023] On the other hand, the application also provides a pump body assembly, which comprises the compressor piston described above, and further comprises:

[0024] A cylinder, which comprises at least one;

[0025] A crankshaft, which is inserted into the cylinder;

[0026] An eccentric part, which is arranged on the crankshaft and located in the cylinder, and comprises at least one, at least one of the eccentric parts is arranged one-to-one with at least one of the cylinders, and the compressor piston is detachably sleeved on the eccentric part and located in the cylinder.

[0027] Further, an annular avoiding step is arranged on the outer periphery of at least one end of the eccentric part.

[0028] In another aspect, the application further provides a compressor comprising the pump body assembly mentioned above, the compressor further comprising at least two eccentric parts, the at least two eccentric parts being arranged along the axial direction of the crankshaft and spaced apart from each other, and the length of the intermediate shaft section between the adjacent two eccentric parts being b;

[0029] The height of the compressor piston along the axial direction of the crankshaft is HP;

[0030] The compressor piston has a second hole section, and the spacing between the second hole section and the end face of the compressor piston along the axial direction of the crankshaft is h;

[0031] Wherein, b, HP and h satisfy the relationship: HP-h≤b≤HP-h+1.4.

[0032] Further, the length b of the intermediate shaft section along the axial direction of the crankshaft satisfies the relationship: 13mm≤b≤14.5mm; and / or,

[0033] The height HP of the compressor piston along the axial direction of the crankshaft satisfies the relationship: 15mm≤HP≤22mm; and / or,

[0034] The spacing h between the second hole section and the end face of the compressor piston along the axial direction of the crankshaft satisfies the relationship: 2.5mm≤h≤3.5mm.

[0035] In the application, when the compressor piston needs to be sleeved on the eccentric part of the crankshaft, the piston body is first inclined so that the first end or the second end of the second hole section is sleeved on the eccentric part, and then the inclination of the piston body is adjusted so that the axial direction of the mounting hole is parallel to the axial direction of the crankshaft, so that the second end or the first end of the second hole section is sleeved on the eccentric part, and then the piston body is moved upward or downward along the axial direction of the mounting hole to sleeve the piston body on the outer peripheral surface of the eccentric part. At the same time, since the outer diameter of the second hole section in the application is larger than the outer diameter of the first hole section, and the second hole section is provided with a chamfer, a recess can be formed on the inner wall surface of the second hole section. The recess can increase the axial dimension of the chamfer along the axial direction of the mounting hole, thereby increasing the moving space of the eccentric part in the second hole section, facilitating the inclined sleeving of the first end or the second end of the second hole section on the eccentric part, and effectively avoiding the collision between the piston body and the eccentric part due to the shortening of the intermediate shaft section of the crankshaft during the installation of the compressor piston, thereby prolonging the service life of the compressor piston to a certain extent. BRIEF DESCRIPTION OF DRAWINGS

[0036] The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:

[0037] Figure 1 A schematic view of a compressor piston according to an embodiment of the application;

[0038] Figure 2 A schematic view of an assembly of a compressor piston and an eccentric part of a crankshaft according to an embodiment of the application.

[0039] In the drawings, the following reference signs are used:

[0040] 10, piston body; 20, mounting hole; 21, first hole section; 22, second hole section; 30, sink; 40, chamfer; 50, crankshaft; 51, eccentric part; 52, intermediate shaft section; h, distance between second hole section and end face of piston body; c, distance between vertex of outer wall face of chamfer and outer wall face of first hole section; HP, height of piston body; d, depth of sink; TP, distance between outer wall face of piston body and outer wall face of first hole section; r, degree of chamfer; b, length of intermediate shaft section between two adjacent eccentric parts. DETAILED DESCRIPTION

[0041] It should be noted that the embodiments and features of the embodiments in the present application can be combined with each other without conflict. The present application will be described in detail below with reference to the accompanying drawings and in conjunction with the embodiments.

[0042] It should be noted that the terms used herein are only intended to describe specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should be understood that, when the term "comprise" and / or "include" is used in this specification, it means that there is a presence of the features, steps, operations, devices, components and / or their combinations.

[0043] The application is not limited by the relative positioning of parts and steps, the numerical expressions, and values set forth in the examples unless otherwise specifically stated. It will be appreciated that the dimensions of the various parts shown in the drawings are not necessarily to scale for ease of illustration. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered part of the specification, where appropriate. In all examples shown and discussed herein, any specific values should be interpreted as merely exemplary and not as a limitation. Thus, other examples of the exemplary embodiments can have different values. It is noted that like numbers and letters refer to like items throughout the several views of the drawings, and once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0044] As mentioned in the background, the existing double-rotor compressor includes a cylinder, a crankshaft, and two pistons, etc., wherein the crankshaft has two eccentric portions, and the outer circumferential surface of each eccentric portion is sleeved with a piston. In order to improve the vibration and noise of the compressor, it is common to shorten the middle shaft section of the crankshaft between the two eccentric portions, but the existing piston is difficult to adapt to the shortened middle shaft section, which is easy to have adverse effects on the vibration and noise of the compressor. For this reason, the inventors of the present application have designed a new type of compressor piston, which can solve the problem that the piston of the double-rotor compressor in the prior art is difficult to adapt to the shortened middle shaft section. The compressor piston of the present application will be described in detail below in conjunction with the drawings.

[0045] Referring to Figures 1 to 2 According to the embodiments of the present application, a compressor piston is provided, which comprises a piston body 10.

[0046] Specifically, the piston body 10 is provided with a mounting hole 20, the mounting hole 20 has a first hole section 21 and a second hole section 22 located at both ends of the first hole section 21, the second hole section 22 is coaxially arranged with the first hole section 21, the outer diameter of the second hole section 22 is larger than that of the first hole section 21, the inner wall surface of the second hole section 22 is provided with a groove 30, and the end of the second hole section 22 away from the first hole section 21 is provided with a chamfer 40. It can be understood that, along the radial direction of the mounting hole 20, both of the second hole sections 22 have a first end and a second end.

[0047] In the present embodiment, when the compressor piston needs to be sleeved on the eccentric portion 51 of the crankshaft 50, the piston body 10 needs to be first inclined, so that the first end or the second end of the second hole section 22 is first sleeved on the eccentric portion 51, and then the inclination of the piston body 10 is adjusted, so that the axial direction of the mounting hole 20 is parallel to the axial direction of the crankshaft 50, so that the second end or the first end of the second hole section 22 is sleeved on the eccentric portion 51, and then the piston body 10 is moved upward or downward along the axial direction of the mounting hole 20, so that the piston body 10 is sleeved on the outer circumferential surface of the eccentric portion 51. At the same time, since the outer diameter of the second hole section 22 in the present embodiment is larger than the outer diameter of the first hole section 21, and the chamfer 40 is arranged on the second hole section 22, a sink groove 30 can be formed on the inner wall surface of the second hole section 22, and the arrangement of the sink groove 30 can increase the axial dimension of the chamfer 40 along the axial direction of the mounting hole 20, thereby increasing the moving space of the eccentric portion 51 in the second hole section 22, facilitating the inclined sleeving of the first end or the second end of the second hole section 22 on the eccentric portion 51, and effectively avoiding the damage of the piston body 10 caused by the collision with the eccentric portion 51 due to the shortening of the intermediate shaft section 52 of the crankshaft 50 during the installation of the compressor piston, thereby prolonging the service life of the compressor piston to a certain extent.

[0048] That is to say, when the compressor piston in the embodiment needs to be sleeved on the eccentric part 51 above the middle shaft section 52, only the piston body 10 needs to be inclined to make the second end of the second hole section 22 above the first hole section 21 first sleeved on one side of the eccentric part 51, then the inclination of the piston body 10 is adjusted to make the axial direction of the mounting hole 20 parallel to the axial direction of the crankshaft 50, so that the first end of the second hole section 22 above the first hole section 21 is also sleeved on the other side of the eccentric part 51, and then the piston body 10 is moved upward along the axial direction of the mounting hole 20 to sleeve the compressor piston on the outer circumferential surface of the eccentric part 51. Similarly, when the compressor piston in the embodiment needs to be sleeved on the eccentric part 51 below the middle shaft section 52, only the piston body 10 needs to be inclined to make the first end of the second hole section 22 below the first hole section 21 first sleeved on one side of the eccentric part 51, then the inclination of the piston body 10 is adjusted to make the axial direction of the mounting hole 20 parallel to the axial direction of the crankshaft 50, so that the second end of the second hole section 22 below the first hole section 21 is also sleeved on the eccentric part 51, and then the piston body 10 is moved downward along the axial direction of the mounting hole 20 to sleeve the compressor piston on the outer circumferential surface of the eccentric part 51. In this process, since the outer diameter of the second hole section 22 in the embodiment is larger than the outer diameter of the first hole section 21, it is convenient to form the sink groove 30 on the inner wall surface of the second hole section 22. The setting of the sink groove 30 can increase the axial dimension of the chamfer 40 along the axial direction of the mounting hole 20, thereby increasing the moving space of the eccentric part 51 in the second hole section 22, facilitating the inclined sleeving of the first end or the second end of the second hole section 22 on the eccentric part 51, and effectively avoiding the damage of the piston body 10 and the eccentric part 51 due to the collision caused by the shortening of the middle shaft section 52 of the crankshaft 50 during the installation of the compressor piston, that is, the compressor piston in the embodiment can adapt to the shortened middle shaft section 52.

[0049] In addition, in the embodiment, the crankshaft 50 is internally provided with an oil supply channel, and an oil outlet hole is arranged on the crankshaft 50 and communicates with the oil supply channel. When the compressor starts to work, the lubricating oil in the compressor is pumped into the oil supply channel under the action of pressure difference, and then flows out through the oil outlet hole and flows to the space between the compressor piston and the eccentric part 51. In this process, since the inner wall surface of the second hole section 22 in the embodiment has the sink groove 30, the setting of the sink groove 30 not only can increase the oil storage space of the second hole section 22, but also can reduce the contact area of the piston body 10 and the eccentric part 51, thereby effectively improving the service life of the compressor piston.

[0050] Further, referring to Figure 1As shown, along the axial direction of the mounting hole 20, the distance between the second hole section 22 and the end face of the piston body 10 in this embodiment is h; along the radial direction of the mounting hole 20, the distance between the vertex of the outer wall surface of the chamfer 40 and the outer wall surface of the first hole section 21 is c; wherein h and c satisfy the relationship: h > c.

[0051] Specifically, in this embodiment, the distance h between the second hole section 22 and the end face of the piston body 10 is the axial depth of the sink 30 along the mounting hole 20, and the distance c between the vertex of the outer wall surface of the chamfer 40 and the outer wall surface of the first hole section 21 is the radial dimension of the chamfer 40 along the radial direction of the mounting hole 20. When h > c, it can be ensured that the lubricating oil in the sink 30 can more effectively cover the end face of the piston body 10 during synchronous rotation of the piston body 10 and the eccentric part 51, thereby reducing the friction and wear between the piston body 10 and the eccentric part 51, and to some extent, prolonging the service life of the compressor piston. At the same time, the smaller radial dimension c of the chamfer 40 can ensure the sealing length of the lubricating oil, that is, the larger axial depth of the sink 30 and the smaller radial dimension of the chamfer 40 help to form a more stable oil film on the end face of the piston body 10, which not only prevents lubricating oil leakage, but also effectively prevents impurities and contaminants from entering between the piston body 10 and the eccentric part 51, thereby protecting the compressor piston from damage.

[0052] Further, referring to Figure 1 As shown, along the axial direction of the mounting hole 20, the height of the piston body 10 in this embodiment is HP; along the axial direction of the mounting hole 20, the distance between the second hole section 22 and the end face of the piston body 10 is h; wherein HP and h satisfy the relationship: h / HP, and 0.275 ≤ h / HP ≤ 0.437, for example, h / HP can be set to 0.275, 0.28, 0.285, 0.29, 0.295, 0.3, 0.31, 0.32, 0.34, 0.36, 0.38, 0.4, 0.41, 0.42, 0.43, 0.437, etc.

[0053] Specifically, when h / HP is less than 0.275, the axial depth of the sink 30 on the second hole section 22 is reduced or the height of the piston body 10 is increased, so that the piston body 10 is easily collided with the eccentric part 51 in the process of being sleeved on the eccentric part 51, and then the intermediate shaft section 52 of the crankshaft 50 cannot be shortened, thereby increasing the vibration and noise of the compressor and adversely affecting the performance of the compressor; when h / HP is greater than 0.437, the axial depth of the sink 30 on the second hole section 22 is increased or the height of the piston body 10 is reduced, resulting in that the contact area between the piston body 10 and the eccentric part 51 is too small, and the local stress during the synchronous rotation of the piston body 10 and the eccentric part 51 is intensified, thereby reducing the service life of the compressor piston. That is to say, in the embodiment, by making HP and h satisfy the relationship: h / HP, and 0.275≤h / HP≤0.437, not only can the shortened intermediate shaft section 52 of the crankshaft 50 be adapted, the vibration and noise of the compressor are reduced, but also the contact area between the piston body 10 and the eccentric part 51 can be ensured, and the service life of the compressor piston is effectively improved.

[0054] Further, referring to Figure 1 As shown in the figure, in the embodiment, the inner wall surface of the second hole section 22 and the outer wall surface of the first hole section 21 form a sink 30, and the depth of the sink 30 along the radial direction of the mounting hole 20 is d; the distance between the outer wall surface of the piston body 10 and the outer wall surface of the first hole section 21 along the radial direction of the mounting hole 20 is TP; the distance between the vertex of the outer wall surface of the chamfer 40 and the outer wall surface of the first hole section 21 along the radial direction of the mounting hole 20 is c; wherein d, c and TP satisfy the relationship: (c+d) / TP, and 0.22≤(c+d) / TP≤0.5, for example, (c+d) / TP can be set to 0.22, 0.24, 0.25, 0.26, 0.28, 0.3, 0.32, 0.34, 0.35, 0.36, 0.38, 0.4, 0.42, 0.44, 0.45, 0.46, 0.48, 0.5, etc.

[0055] Specifically, the distance c between the vertex of the outer wall surface of the chamfer 40 and the outer wall surface of the first hole section 21 is the radial dimension of the chamfer 40, and the distance TP between the outer wall surface of the piston body 10 and the outer wall surface of the first hole section 21 is the wall thickness of the piston body 10, wherein the radial dimension c of the chamfer 40 is related to the sealing length, and the depth d of the sink 30 is related to the oil storage space. When (c+d) / TP is less than 0.22, the radial dimension of the chamfer 40 is reduced, or the radial width dimension of the sink 30 is reduced, or the wall thickness of the piston body 10 is increased, at this time, although the sealing length of the compressor piston is effectively ensured, the oil storage space of the sink 30 is reduced and the contact area between the compressor piston and the eccentric part 51 is increased, which reduces the lubrication effect of the lubricating oil and causes the compressor piston to be worn; when (c+d) / TP is greater than 0.5, the radial dimension of the chamfer 40 is increased, or the radial width dimension of the sink 30 is increased, or the wall thickness of the piston body 10 is reduced, at this time, although the oil storage space of the lubricating oil is increased with the increase of the radial dimension of the chamfer 40, the increase of the radial width dimension of the sink 30 cannot ensure the sealing length, and the reduction of the wall thickness of the piston body 10 increases the volume of the mounting hole 20 as a whole, thereby causing the contact area between the piston body 10 and the eccentric part 51 to be too small, intensifying the local stress during the synchronous rotation of the piston body 10 and the eccentric part 51, and reducing the service life of the compressor piston.

[0056] Further, along the radial direction of the mounting hole 20, the distance c between the vertex of the outer wall surface of the chamfer 40 and the outer wall surface of the first hole section 21 in the present embodiment satisfies the relationship: c≥0.5mm, for example, c can be 0.5mm, 0.7mm, 0.9mm, 1mm, 1.2mm, 1.4mm, 1.6mm, 1.8mm, 2mm, 2.2mm, 2.4mm, 2.5mm, etc. When c is less than 0.5mm, not only the machining difficulty of the chamfer 40 is increased, but also the sealing length of the lubricating oil is difficult to ensure, thereby making it difficult to improve the lubrication effect of the end surface of the piston body 10. That is, by making the distance c between the vertex of the outer wall surface of the chamfer 40 and the outer wall surface of the first hole section 21 satisfy the relationship: c≥0.5mm in the present embodiment, not only the sealing length of the lubricating oil can be ensured, but also the machining difficulty of the chamfer 40 is reduced.

[0057] Further, along the axial direction of the mounting hole 20, the spacing h between the second hole section 22 and the end face of the piston body 10 in the embodiment satisfies the relationship: 2.5 mm≤h≤3.5 mm, for example, h can be 2.5 mm, 2.6 mm, 2.7 mm, 2.8 mm, 2.9 mm, 3 mm, 3.1 mm, 3.2 mm, 3.3 mm, 3.4 mm, 3.5 mm, etc. When h is less than 2.5 mm, the axial depth of the sink 30 on the second hole section 22 is shortened, which is prone to collide with the eccentric part 51 during the process of the piston body 10 being sleeved on the eccentric part 51, thereby failing to shorten the intermediate shaft section 52 of the crankshaft 50, and further increasing the vibration and noise of the compressor, which adversely affects the performance of the compressor. When h is greater than 3.5 mm, the axial depth of the sink 30 on the second hole section 22 is increased, which leads to too small contact area between the piston body 10 and the eccentric part 51, and aggravates the local stress during the synchronous rotation of the piston body 10 and the eccentric part 51, thereby reducing the service life of the compressor piston.

[0058] Further, along the radial direction of the mounting hole 20, the depth d of the sink 30 in the embodiment satisfies the relationship: 0.7 mm≤d≤1 mm, for example, d can be 0.7 mm, 0.75 mm, 0.8 mm, 0.85 mm, 0.9 mm, 0.95 mm, 1 mm, etc. When d is less than 0.7 mm, the oil storage space of the sink 30 for lubricating oil is reduced, which is prone to cause that the lubricating oil cannot fully cover all friction surfaces of the compressor piston and the eccentric part 51 during the long-time operation of the compressor, thereby accelerating the wear of the compressor piston and the eccentric part 51. When d is greater than 1 mm, although the oil storage space of the sink 30 for lubricating oil is increased, it is difficult to ensure the sealing length of the lubricating oil. That is to say, by making the depth d of the sink 30 along the radial direction of the mounting hole 20 satisfy the relationship: 0.7 mm≤d≤1 mm in the embodiment, not only the oil storage space can be increased to improve the lubrication effect of the end face of the piston body 10, but also the sealing length of the lubricating oil can be ensured, thereby effectively improving the service life of the compressor piston.

[0059] Further, along the axial direction of the mounting hole 20, the height HP of the piston body 10 in the embodiment satisfies the relationship: 15 mm≤HP≤22 mm, for example, HP can be 15 mm, 16 mm, 17 mm, 18 mm, 19 mm, 20 mm, 21 mm, 22 mm, etc.

[0060] Specifically, when the HP is less than 15 mm, the piston body 10 is prone to collide with the eccentric part 51 when the piston body 10 is sleeved on the eccentric part 51, and then the shortened middle shaft section 52 of the crankshaft 50 cannot be matched, thereby increasing the vibration and noise of the compressor and adversely affecting the performance of the compressor. At the same time, the HP less than 15 mm reduces the stroke length of the piston body 10, thereby reducing the amount of gas suction and exhaust per cycle and reducing the efficiency of the compressor. When the HP is greater than 22 mm, the contact area between the piston body 10 and the eccentric part 51 is too small, which intensifies the local stress of the piston body 10 during synchronous rotation with the eccentric part 51, thereby reducing the service life of the compressor piston. At the same time, the higher piston body 10 also reduces the space utilization rate inside the compressor. That is to say, by making the height HP of the piston body 10 along the axial direction of the mounting hole 20 satisfy the relationship 15 mm≤HP≤22 mm in the embodiment, the shortened middle shaft section 52 of the crankshaft 50 can be matched, and the vibration and noise of the compressor are improved.

[0061] Further, along the radial direction of the mounting hole 20, the distance TP between the outer wall surface of the piston body 10 and the outer wall surface of the first hole section 21 in the embodiment satisfies the relationship 5.5 mm≤TP≤7.5 mm, for example, TP can be 5.5 mm, 5.7 mm, 5.9 mm, 6 mm, 6.2 mm, 6.4 mm, 6.6 mm, 6.8 mm, 7 mm, 7.2 mm, 7.4 mm, 7.5 mm, etc.

[0062] Specifically, when TP is less than 5.5 mm, the wall thickness of the piston body 10 is too thin, which reduces the pressure bearing capacity of the piston body 10, thereby causing the piston body 10 to be prone to deformation or fracture during high-speed operation of the compressor, thereby affecting the normal operation and service life of the compressor. At the same time, the too thin wall thickness of the piston body 10 is prone to increase the vibration and noise of the compressor during operation. When TP is greater than 7.5 mm, the wall thickness of the piston body 10 is too thick, which increases the manufacturing cost of the compressor piston and reduces the space utilization rate inside the compressor. That is to say, by making the distance TP between the outer wall surface of the piston body 10 and the outer wall surface of the first hole section 21 along the radial direction of the mounting hole 20 satisfy the relationship 5.5 mm≤TP≤7.5 mm in the embodiment, not only the pressure bearing capacity of the piston body 10 can be improved, the service life of the compressor piston is prolonged, but also the manufacturing cost of the compressor piston can be reduced, and the space utilization rate inside the compressor can be effectively improved.

[0063] Further, the degree r of the chamfer 40 in the embodiment satisfies the relationship: r≤20°, for example, 20°, 19°, 18°, 17°, 16°, 15°, 14°, 13°, 12°, 11°, 10°, etc. Specifically, when r is greater than 20°, it is difficult to form an oil wedge at the contact end face between the piston body 10 and the bearing during the operation of the compressor piston, thereby reducing the oil film stiffness at the contact end face and shortening the service life of the compressor piston. That is to say, by making the degree r of the chamfer 40 satisfy the relationship: r≤20°, the embodiment can form an oil wedge at the contact end face between the piston body 10 and the bearing during the operation of the compressor piston, thereby passively pressing the lubricating oil into the contact end face, improving the oil film stiffness at the contact end face, effectively improving the lubrication effect, and improving the service life of the compressor piston.

[0064] On the other hand, the embodiment of the present application also provides a pump body assembly, which comprises the compressor piston described above, and therefore, the pump body assembly comprises all the technical effects of the compressor piston. Since the technical effects of the compressor piston have been described in detail above, they will not be described here again.

[0065] Further, referring to Figure 2 , the pump body assembly in the embodiment further comprises a cylinder (not shown in the drawings), a crankshaft 50, and an eccentric part 51. The cylinder comprises at least one; the crankshaft 50 is inserted into the cylinder; the eccentric part 51 is arranged on the crankshaft 50 and located in the cylinder, and the eccentric part 51 comprises at least one, at least one eccentric part 51 is arranged in one-to-one correspondence with at least one cylinder, and the compressor piston is detachably sleeved on the eccentric part 51 and located in the cylinder.

[0066] Specifically, the compressor piston can perform accurate reciprocating motion in the cylinder under the driving of the eccentric part 51, thereby compressing the gas and effectively improving the compression efficiency of the compressor as a whole. At the same time, since the rolling friction exists between the compressor piston and the eccentric part 51, the wear caused by the rolling friction is smaller than that caused by the sliding friction, which helps to prolong the service life of the pump body assembly, and the rolling motion of the compressor piston is more stable than the sliding motion, so that the noise and vibration generated by the pump body assembly during operation can be significantly reduced.

[0067] Optionally, the eccentric part 51 and the cylinder in the embodiment can be provided as one, two or more. The following Figure 2 embodiments of the present application show the case where the eccentric part 51 is provided as two.

[0068] Furthermore, in this embodiment, an annular clearance step (not shown in the accompanying drawings) is provided on the outer periphery of at least one end of the eccentric portion 51. Specifically, in this embodiment, the setting of the groove 30 can increase the oil storage space of the compressor piston. Based on this, this embodiment further increases the oil storage space by providing an annular clearance step on the outer periphery of at least one end of the eccentric portion 51, so that the lubricating oil can be more concentratedly distributed on the outer peripheral surface of the eccentric portion 51, improving the lubrication conditions, reducing the friction and wear between the compressor piston and the eccentric portion 51, and reducing the vibration and noise during compressor operation.

[0069] Furthermore, this application also provides a compressor that includes the aforementioned pump assembly. Therefore, this compressor incorporates all the technical effects of the aforementioned pump assembly. Since the technical effects of the pump assembly have already been described in detail above, they will not be repeated here.

[0070] Further, see Figure 2 As shown, the compressor in this embodiment further includes at least two eccentric portions 51, which are spaced apart along the axial direction of the crankshaft 50. The length of the intermediate shaft section 52 between two adjacent eccentric portions 51 is b. The height of the compressor piston along the axial direction of the crankshaft 50 is HP. The compressor piston has a second bore section 22, and the distance between the second bore section 22 and the end face of the compressor piston along the axial direction of the crankshaft 50 is h. Wherein, b, HP and h satisfy the relationship: HP-h≤b≤HP-h+1.4.

[0071] Specifically, by controlling the range of the length b of the intermediate shaft section 52, a reasonable interval between the two eccentric parts 51 is ensured. This not only helps maintain the compactness of the compressor structure but also avoids mechanical interference or increased friction caused by excessively dense eccentric parts 51. Simultaneously, a reasonable interval between the eccentric parts 51 enhances the overall rigidity and stability of the compressor, reducing vibration and noise during high-speed operation and effectively improving the compressor's efficiency and service life. Meanwhile, by setting the groove 30 and controlling its axial depth h, lubricating oil can be effectively guided to critical parts to reduce wear. In other words, because there is a certain adjustment range between b, HP, and h in this embodiment, the compressor can adapt to different operating conditions, thereby reducing compressor vibration and noise while ensuring compressor performance.

[0072] Further, see Figure 2 As shown, along the axial direction of the crankshaft 50, the length b of the intermediate shaft segment 52 in this embodiment satisfies the relationship: 13mm≤b≤14.5mm. For example, b can be 13mm, 13.2mm, 13.4mm, 13.6mm, 13.8mm, 14mm, 14.2mm, 14.4mm, 14.5mm, etc.

[0073] Specifically, when b is less than 13 mm, not only will the distance between the two eccentric portions 51 become more compact, leading to mechanical interference between the two eccentric portions 51 due to vibration and thermal expansion and other factors during high-speed operation of the compressor, thereby increasing friction and wear, but also the overall rigidity of the crankshaft 50 will be weakened, resulting in greater vibration and noise during operation of the compressor, affecting the normal operation of the compressor; when b is greater than 14.5 mm, although the distance between the two eccentric portions 51 can be increased to reduce the risk of mechanical interference, the excessively long intermediate shaft section 52 will also cause the overall rigidity of the crankshaft 50 to decrease, which will also affect the stability and reliability of the compressor, and at the same time, the excessively long intermediate shaft section 52 will increase the moment of inertia of the crankshaft 50, resulting in increased energy consumption and reduced energy efficiency of the compressor. That is to say, by making the length b of the intermediate shaft section 52 along the axial direction of the crankshaft 50 satisfy the relationship: 13 mm≤b≤14.5 mm in the present embodiment, not only can mechanical interference between the two eccentric portions 51 be avoided, reducing friction and wear, but also the overall rigidity of the crankshaft 50 can be ensured, reducing the vibration and noise generated by the crankshaft 50 during operation of the compressor.

[0074] Further, along the axial direction of the crankshaft 50, the height HP of the compressor piston in the present embodiment satisfies the relationship: 15 mm≤HP≤22 mm, for example, HP can be 15 mm, 16 mm, 17 mm, 18 mm, 19 mm, 20 mm, 21 mm, 22 mm, etc.

[0075] Specifically, when HP is less than 15 mm, the compressor piston is prone to collide with the eccentric portion 51 when it is sleeved on the eccentric portion 51, which in turn cannot be adapted to shorten the intermediate shaft section 52 of the crankshaft 50, thereby increasing the vibration and noise of the compressor and adversely affecting the performance of the compressor, and at the same time, HP less than 15 mm will reduce the stroke length of the compressor piston, resulting in a decrease in the amount of gas inhaled and expelled per cycle, thereby reducing the efficiency of the compressor; when HP is greater than 22 mm, the contact area between the compressor piston and the eccentric portion 51 is too small, which exacerbates the local stress during synchronous rotation of the compressor piston and the eccentric portion 51, thereby reducing the service life of the compressor piston, and at the same time, a higher compressor piston will also reduce the space utilization rate inside the compressor. That is to say, by making the height HP of the compressor piston along the axial direction of the mounting hole 20 satisfy the relationship: 15 mm≤HP≤22 mm in the present embodiment, the shortened intermediate shaft section 52 can be adapted, and the vibration and noise of the compressor can be improved.

[0076] Further, along the axial direction of the crankshaft 50, the spacing h between the second hole section 22 and the end surface of the compressor piston in the embodiment satisfies the relationship: 2.5mm≤h≤3.5mm, for example, h can be 2.5mm, 2.6mm, 2.7mm, 2.8mm, 2.9mm, 3mm, 3.1mm, 3.2mm, 3.3mm, 3.4mm, 3.5mm, etc.

[0077] Specifically, when h is less than 2.5mm, the axial depth of the sink 30 on the second hole section 22 is shortened, so that the compressor piston is prone to collide with the eccentric part 51 during the process of being sleeved on the eccentric part 51, and then the intermediate shaft section 52 of the crankshaft 50 cannot be shortened, thereby increasing the vibration and noise of the compressor and adversely affecting the performance of the compressor; when h is greater than 3.5mm, the axial depth of the sink 30 on the second hole section 22 is increased, which leads to too small contact area between the compressor piston and the eccentric part 51, and aggravates the local stress during the synchronous rotation of the compressor piston and the eccentric part 51, thereby reducing the service life of the compressor piston.

[0078] For the purpose of convenience and brevity, spatially relative terms, such as "above", "below", "upper", "lower", and the like, can be used herein for describing the orientation of one device or element versus another device or element as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the devices in their use or operation in different ways. For example, if a device in the figures is inverted, then a device described as "above" or "above" other devices or structures can be oriented "below" other devices or structures. Accordingly, the exemplary term "above" can encompass both an orientation of above and below. The devices can be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

[0079] In addition, it should be noted that the use of "first", "second", and the like words to qualify elements is merely for the convenience of distinguishing the corresponding elements, and the above words have no special meaning unless otherwise stated, and therefore cannot be understood as limiting the scope of protection of the present application.

[0080] The above only is the preferred embodiment of the present application, and is not used to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A compressor piston characterized by, The piston body (10) is provided with a mounting hole (20), the mounting hole (20) has a first hole section (21) and a second hole section (22) located at both ends of the first hole section (21), the second hole section (22) is coaxially arranged with the first hole section (21), the outer diameter of the second hole section (22) is greater than that of the first hole section (21), the inner wall surface of the second hole section (22) is provided with a groove (30), and the end of the second hole section (22) away from the first hole section (21) is provided with a chamfer (40). Along the axial direction of the mounting hole (20), the distance between the second hole section (22) and the end surface of the piston body (10) is h; 2. The compressor piston of claim 1, wherein Along the radial direction of the mounting hole (20), the distance between the vertex of the outer wall surface of the chamfer (40) and the outer wall surface of the first hole section (21) is c; Wherein, h and c satisfy the relationship: h>c. Along the axial direction of the mounting hole (20), the height of the piston body (10) is HP; 3. The compressor piston of claim 1, wherein, Along the axial direction of the mounting hole (20), the distance between the second hole section (22) and the end surface of the piston body (10) is h; Wherein, HP and h satisfy the relationship: h / HP, and 0.275≤h / HP≤0.

437. The inner wall surface of the second hole section (22) and the outer wall surface of the first hole section (21) form the groove (30), and along the radial direction of the mounting hole (20), the depth of the groove (30) is d; 4. The compressor piston of claim 1, wherein, Along the radial direction of the mounting hole (20), the distance between the outer wall surface of the piston body (10) and the outer wall surface of the first hole section (21) is TP; Along the radial direction of the mounting hole (20), the distance between the vertex of the outer wall surface of the chamfer (40) and the outer wall surface of the first hole section (21) is c; Wherein, d, c and TP satisfy the relationship: (c+d) / TP, and 0.22≤(c+d) / TP≤0.

5. Along the radial direction of the mounting hole (20), the distance c between the vertex of the outer wall surface of the chamfer (40) and the outer wall surface of the first hole section (21) satisfies the relationship: c≥0.5mm; and / or, 5. The compressor piston of any one of claims 1 to 4, wherein, Along the axial direction of the mounting hole (20), the distance h between the second hole section (22) and the end surface of the piston body (10) satisfies the relationship: 2.5mm≤h≤3.5mm; and / or, Along the radial direction of the mounting hole (20), the depth d of the groove (30) satisfies the relationship: 0.7mm≤d≤1mm; and / or, Along the axial direction of the mounting hole (20), the height HP of the piston body (10) satisfies the relationship: 15mm≤HP≤22mm; and / or, Along the radial direction of the mounting hole (20), the distance TP between the outer wall surface of the piston body (10) and the outer wall surface of the first hole section (21) satisfies the relationship: 5.5mm≤TP≤7.5mm. The degree r of the chamfer (40) satisfies the relationship: r≤20°.

6. The compressor piston of any one of claims 1 to 4, wherein, ​ 7. A pump body assembly characterized by, The pump body assembly comprises the compressor piston according to any one of claims 1 to 6, and further comprises: a cylinder, the cylinder comprising at least one; a crankshaft (50) inserted into the cylinder; an eccentric portion (51) arranged on the crankshaft (50) and located in the cylinder, the eccentric portion (51) comprising at least one, at least one of the eccentric portions (51) being arranged in one-to-one correspondence with at least one of the cylinders, and the compressor piston being detachably sleeved on the eccentric portion (51) and located in the cylinder.

8. The pump body assembly of claim 7, wherein, An annular avoiding step is arranged on the outer periphery of at least one end of the eccentric portion (51).

9. A compressor characterized by, The compressor comprises the pump body assembly according to any one of claims 7 to 8, and further comprises at least two eccentric portions (51), the at least two eccentric portions (51) being arranged in an axial direction of the crankshaft (50) at intervals, and the length of the intermediate shaft section (52) between the adjacent two eccentric portions (51) being b; The height of the compressor piston in the axial direction of the crankshaft (50) is HP; The compressor piston has a second hole section (22), and the spacing between the second hole section (22) and the end surface of the compressor piston in the axial direction of the crankshaft (50) is h; wherein b, HP and h satisfy the relationship: HP-h≤b≤HP-h+1.

4.

10. The compressor of claim 9, wherein, The length b of the intermediate shaft section (52) in the axial direction of the crankshaft (50) satisfies the relationship: 13mm≤b≤14.5mm; and / or, The height HP of the compressor piston in the axial direction of the crankshaft (50) satisfies the relationship: 15mm≤HP≤22mm; and / or, The spacing h between the second hole section (22) and the end surface of the compressor piston in the axial direction of the crankshaft (50) satisfies the relationship: 2.5mm≤h≤3.5mm.

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