WO2022142336A1

WO2022142336A1 - Flange structure, pump assembly, and fluid machine

Info

Publication number: WO2022142336A1
Application number: PCT/CN2021/110075
Authority: WO
Inventors: 胡余生; 魏会军; 徐嘉; 杜忠诚; 任丽萍
Original assignee: 珠海格力电器股份有限公司
Priority date: 2020-12-29
Filing date: 2021-08-02
Publication date: 2022-07-07
Also published as: CN114688028A

Abstract

A flange structure, a pump assembly, and a fluid machine. The side of the flange structure facing a cylinder jacket (40) is provided with a muffler channel; the muffler channel extends along the circumferential direction of the flange structure; the flange structure also comprises flange vent holes (5011); and the flange vent holes (5011) are communicated with the muffler channel. The flange structure has a noise reduction function, such that gas flow noise is effectively reduced.

Description

法兰结构、泵体组件和流体机械Flange structure, pump body components and fluid machinery

相关申请Related applications

本申请是以申请号为202011590366.0，申请日为2020年12月29日，发明名称为“法兰结构、泵体组件和流体机械”的中国专利申请为基础，并主张其优先权，该中国专利申请的公开内容在此作为整体引入本申请中。This application is based on the Chinese patent application with the application number of 202011590366.0 and the application date of December 29, 2020, and the name of the invention is "flange structure, pump body assembly and fluid machinery", and claims its priority. The disclosure of the application is hereby incorporated into this application in its entirety.

技术领域technical field

本公开涉及转缸压缩机相关技术领域，具体而言，涉及一种法兰结构、泵体组件和流体机械。The present disclosure relates to the related technical field of rotary cylinder compressors, and in particular, to a flange structure, a pump body assembly and a fluid machine.

背景技术Background technique

以转缸压缩机为例，目前现有的压缩机的泵体组件为达到降低噪音的效果，通常是在将上法兰的外部设置额外的消音器，上法兰仅提供排气孔，保证气缸内的气体可以顺利的通过上法兰向外流出，从而在消音器中进行消音。Taking the rotary cylinder compressor as an example, in order to achieve the effect of reducing noise in the pump body components of the existing compressor, an additional muffler is usually arranged outside the upper flange, and the upper flange only provides an exhaust hole to ensure The gas in the cylinder can smoothly flow out through the upper flange, so as to be muffled in the muffler.

这样结构的泵体组件，结构较为复杂，且上法兰的作用单一，无法实现消音的功能。The structure of the pump body assembly with such a structure is relatively complex, and the function of the upper flange is single, and the function of noise reduction cannot be realized.

由上可知，目前现有的转缸压缩机在运行过程中，法兰结构不具有消音功能。It can be seen from the above that the flange structure of the existing rotary cylinder compressor does not have the function of silencing during operation.

发明内容SUMMARY OF THE INVENTION

本公开的主要目的在于提供一种法兰结构、泵体组件和流体机械，以改善现有的法兰结构不具有消音功能的问题。The main purpose of the present disclosure is to provide a flange structure, a pump body assembly and a fluid machine, so as to improve the problem that the existing flange structure does not have a sound-absorbing function.

为了实现上述目的，根据本公开的一个方面，提供了一种法兰结构，法兰结构朝向气缸套的一侧开设有消音通道，消音通道沿法兰结构的周向延伸，法兰结构还包括法兰排气孔，法兰排气孔与消音通道连通。In order to achieve the above object, according to an aspect of the present disclosure, a flange structure is provided, a side of the flange structure facing the cylinder liner is provided with a muffler channel, the muffler channel extends along the circumferential direction of the flange structure, and the flange structure further includes The flange exhaust hole is connected with the muffler channel.

在一些实施例中，消音通道首尾连通，或消音通道的首尾不连通。In some embodiments, the silencer channels are connected end to end, or the silencer channels are not connected end to end.

在一些实施例中，消音通道由一个连续的消音凹槽构成。In some embodiments, the muffling channel is formed by a continuous muffling groove.

在一些实施例中，消音凹槽的侧壁具有向法兰结构的中心轴突出的筋状结构，筋状结构为多个，多个筋状结构沿消音凹槽的侧壁间隔设置，以使消音通道具有交替设置的宽过流区域和窄过流区域。In some embodiments, the side wall of the muffler groove has a rib-like structure protruding toward the central axis of the flange structure, and there are multiple rib-shaped structures, and the plurality of rib-shaped structures are spaced along the side wall of the muffler groove, so that the The muffler channel has alternating wide and narrow overcurrent regions.

在一些实施例中，不同的筋状结构与法兰结构的中心轴之间的距离相等；或者至少两个筋状结构与法兰结构的中心轴之间的距离不相等。In some embodiments, the distances between different tendon structures and the central axis of the flange structure are equal; or the distances between at least two tendon structures and the central axis of the flange structure are unequal.

在一些实施例中，筋状结构的个数大于3个且小于5个。In some embodiments, the number of tendon structures is greater than 3 and less than 5.

在一些实施例中，法兰结构具有多个消音凹槽，多个消音凹槽沿法兰结构的周向间隔设置，且相邻两个消音凹槽通过连通孔连通。In some embodiments, the flange structure has a plurality of sound-absorbing grooves, the plurality of sound-absorbing grooves are arranged at intervals along the circumferential direction of the flange structure, and two adjacent sound-absorbing grooves are communicated through a communication hole.

在一些实施例中，法兰结构具有法兰孔，法兰孔与法兰结构的中心轴偏心设置。In some embodiments, the flange structure has a flange hole, and the flange hole and the central axis of the flange structure are arranged eccentrically.

在一些实施例中，法兰结构的中部具有轴颈，轴颈由开设消音通道后的部分构成，法兰孔贯穿轴颈的轴向端面。In some embodiments, a shaft journal is provided in the middle of the flange structure, the journal is formed by the part after the muffler channel is opened, and the flange hole penetrates the axial end face of the journal.

在一些实施例中，轴颈的外周圆与法兰结构的外周圆同轴。In some embodiments, the outer circumference of the journal is coaxial with the outer circumference of the flange structure.

在一些实施例中，轴颈背离气缸套的一侧具有突出于法兰结构的端面的凸环结构，以使法兰结构的轴向上的总高度H大于法兰结构的轴向上的两端面之间的高度H1，消音通道在法兰结构的轴向上的高度H2小于法兰结构的轴向上的两端面之间的高度H1。In some embodiments, the side of the journal facing away from the cylinder liner has a convex ring structure protruding from the end face of the flange structure, so that the total height H of the flange structure in the axial direction is greater than the two axial heights of the flange structure. The height H1 between the end faces and the height H2 of the muffler passage in the axial direction of the flange structure are smaller than the height H1 between the two end faces of the flange structure in the axial direction.

在一些实施例中，0.5H<H1<0.9H；和/或0.3H<H2<0.7H。In some embodiments, 0.5H<H1<0.9H; and/or 0.3H<H2<0.7H.

在一些实施例中，0.65H<H1<0.75H；和/或0.4H<H2<0.6H。In some embodiments, 0.65H<H1<0.75H; and/or 0.4H<H2<0.6H.

在一些实施例中，法兰结构的侧壁厚度L1、法兰结构的端面厚度L2满足如下的关系：0.05H<L1<0.25H；0.1H<L2<0.4H。In some embodiments, the thickness L1 of the side wall of the flange structure and the thickness L2 of the end surface of the flange structure satisfy the following relationship: 0.05H<L1<0.25H; 0.1H<L2<0.4H.

在一些实施例中，消音通道的侧壁具有向法兰结构的中心轴突出的筋状结构，轴颈的轴向端面的最小厚度L3与筋状结构至轴颈的中心k2之间的距离R3之间的关系为0.05H<L3<R3。In some embodiments, the side wall of the muffler channel has a rib-like structure protruding toward the central axis of the flange structure, the minimum thickness L3 of the axial end face of the journal and the distance R3 between the rib-like structure and the center k2 of the journal The relationship between them is 0.05H<L3<R3.

在一些实施例中，法兰结构的中部具有轴颈，轴颈的中心k2与法兰结构的法兰轴孔中心k1之间具有偏心量e，法兰结构的法兰轴孔中心k1与消音凹槽的外侧槽壁之间的距离为R1，筋状结构至轴颈的中心k2的距离为R3，由轴颈的中心k2至消音凹槽的内侧槽壁之间的距离为R2，且R1、R2、R3之间满足如下关系：0.1<(R1-R2)/(R3-R2)<0.4。In some embodiments, there is a journal in the middle of the flange structure, and there is an eccentricity e between the center k2 of the journal and the center k1 of the flange shaft hole of the flange structure. The distance between the outer groove walls of the groove is R1, the distance from the tendon structure to the center k2 of the journal is R3, the distance from the center k2 of the journal to the inner groove wall of the muffler groove is R2, and R1 , R2 and R3 satisfy the following relationship: 0.1<(R1-R2)/(R3-R2)<0.4.

在一些实施例中，0.15<(R1-R2)/(R3-R2)<0.25。In some embodiments, 0.15<(R1-R2)/(R3-R2)<0.25.

在一些实施例中，各宽过流区域处的距离R1均相等，以构成参考第一参考圆；各窄过流区域处的距离R3均相等，以构成参考第二参考圆；各宽过流区域和窄过流区域处的距离R2均相等，以构成参考第三参考圆。In some embodiments, the distances R1 at the wide overcurrent regions are all equal to form a reference first reference circle; the distances R3 at each narrow overcurrent region are equal to form a reference second reference circle; The distance R2 at both the area and the narrow overcurrent area is equal to form a reference third reference circle.

在一些实施例中，法兰结构为上法兰。In some embodiments, the flange structure is an upper flange.

根据本公开的另一方面，提供了一种泵体组件，泵体组件包括法兰结构。According to another aspect of the present disclosure, a pump body assembly is provided that includes a flange structure.

在一些实施例中，泵体组件还包括：转轴；限位板，限位板具有限位板排气孔；气缸套，气缸套具有气缸套排气孔，转轴依次穿过法兰结构、限位板和气缸套，气缸套排气孔、限位板排气孔和法兰结构的消音通道连通。In some embodiments, the pump body assembly further includes: a rotating shaft; a limit plate, the limit plate has a limit plate exhaust hole; a cylinder liner, the cylinder liner has a cylinder liner exhaust hole, the rotating shaft sequentially passes through the flange structure, the limit plate The position plate and the cylinder liner are connected with the exhaust hole of the cylinder liner, the exhaust hole of the limit plate and the muffler channel of the flange structure.

在一些实施例中，气缸套具有容积腔泵体组件还包括：气缸，气缸可转动地设置在容积腔内，气缸上沿其径向开设有活塞孔；活塞，活塞具有滑移孔，转轴的至少一部分穿设在滑移孔内，活塞随转轴转动的过程中，活塞相对于转轴在活塞孔内滑动，且气缸同步转动。In some embodiments, the cylinder liner has a volume cavity and the pump body assembly further includes: a cylinder, the cylinder is rotatably arranged in the volume cavity, and a piston hole is opened on the cylinder along its radial direction; At least a part is penetrated in the sliding hole. During the process of the piston rotating with the rotating shaft, the piston slides in the piston hole relative to the rotating shaft, and the cylinder rotates synchronously.

在一些实施例中，限位板排气孔为多个，多个限位板排气孔间隔设置。In some embodiments, there are a plurality of air vent holes in the limit plate, and the plurality of air holes in the limit plate are arranged at intervals.

在一些实施例中，至少两个限位板排气孔的大小不同。In some embodiments, the vent holes of the at least two stopper plates are different in size.

在一些实施例中，气缸套排气孔为多个，气缸套具有多个中间腔，各中间腔均通过对应的气缸套排气孔与气缸套的容积腔连通，气缸套还具有与各中间腔连通的多个气缸套连通孔，多个气缸套连通孔与多个限位板排气孔一一对应设置。In some embodiments, the cylinder liner has a plurality of exhaust holes, the cylinder liner has a plurality of intermediate cavities, and each intermediate cavity is communicated with the volume cavity of the cylinder liner through the corresponding cylinder liner exhaust hole, and the cylinder liner also has a space with each intermediate cavity. There are a plurality of cylinder liner communication holes connected to the cavity, and the plurality of cylinder liner communication holes are arranged in a one-to-one correspondence with the plurality of limit plate exhaust holes.

在一些实施例中，多个气缸套排气孔中的至少两个气缸套排气孔的大小不同；和/或各中间腔彼此不连通；和/或多个气缸套连通孔的至少两个气缸套连通孔的大小不同。In some embodiments, at least two of the plurality of cylinder liner exhaust holes are of different sizes; and/or the intermediate cavities are not in communication with each other; and/or at least two of the plurality of cylinder liner communication holes The size of the cylinder liner communication holes is different.

在一些实施例中，限位板排气孔与法兰结构的法兰排气孔在法兰结构的周向上间隔设置。In some embodiments, the limiting plate vent holes and the flange vent holes of the flange structure are spaced apart in the circumferential direction of the flange structure.

在一些实施例中，限位板排气孔与法兰排气孔在法兰结构的周向上间隔角度160度至200度。In some embodiments, the vent hole of the limiting plate and the vent hole of the flange are spaced at an angle of 160 degrees to 200 degrees in the circumferential direction of the flange structure.

根据本公开的另一方面，提供了一种流体机械，流体机械包括泵体组件。According to another aspect of the present disclosure, a fluid machine is provided that includes a pump body assembly.

应用本公开的技术方案，法兰结构朝向气缸套的一侧开设有消音通道，消音通道沿法兰结构的周向延伸，法兰结构还包括法兰排气孔，法兰排气孔与消音通道连通。Applying the technical solution of the present disclosure, the side of the flange structure facing the cylinder liner is provided with a muffler channel, the muffler channel extends along the circumferential direction of the flange structure, and the flange structure further includes a flange exhaust hole, a flange exhaust hole and a muffler. channel connection.

由上可知，从以上的描述中，可以看出，本公开上述实施例中，通过在法兰结构的一侧设置周向延伸的消音通道，以使现法兰结构具有消音功能，周向延伸的消音通道增大了气体的流动路径，有效减小了气体流动的噪音。现有的转缸压缩机需要与消音器配合使用以进行降噪消音，现有的转缸压缩机的法兰结构不具有消音功能。As can be seen from the above, from the above description, it can be seen that in the above-mentioned embodiments of the present disclosure, a circumferentially extending silencing channel is arranged on one side of the flange structure, so that the existing flange structure has a silencing function, which extends circumferentially. The muffler channel increases the flow path of the gas and effectively reduces the noise of the gas flow. The existing rotary cylinder compressor needs to be used in conjunction with a muffler for noise reduction and noise reduction, and the flange structure of the existing rotary cylinder compressor does not have a noise reduction function.

具体地，泵体组件产生的高压气体流入到法兰结构的消音通道内，并沿着消音通道周向流动，流动至法兰排气孔处，经法兰排气孔排出。有效降低了气动声噪，以使法兰结构具有消音功能。Specifically, the high-pressure gas generated by the pump body assembly flows into the muffler passage of the flange structure, flows along the circumferential direction of the muffler passage, flows to the flange exhaust hole, and is discharged through the flange exhaust hole. The aerodynamic noise is effectively reduced, so that the flange structure has the function of silencing.

附图说明Description of drawings

构成本申请的一部分的说明书附图用来提供对本公开的进一步理解，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：The accompanying drawings forming a part of the present application are used to provide further understanding of the present disclosure, and the exemplary embodiments of the present disclosure and their descriptions are used to explain the present disclosure and do not constitute an improper limitation of the present disclosure. In the attached image:

图1示出了根据本公开的泵体组件的安装关系示意图；以及FIG. 1 shows a schematic diagram of the installation relationship of the pump body assembly according to the present disclosure; and

图2示出了图1中的气缸套的剖视图；Figure 2 shows a cross-sectional view of the cylinder liner of Figure 1;

图3示出了图1中的气缸套的示意图；Figure 3 shows a schematic diagram of the cylinder liner in Figure 1;

图4示出了本公开的法兰结构上设置消音凹槽的示意图，其中消音凹槽首尾连通；FIG. 4 shows a schematic diagram of setting a muffler groove on the flange structure of the present disclosure, wherein the muffler groove is connected end to end;

图5示出了本公开的法兰结构上设置消音凹槽的示意图，其中消音凹槽首尾间设置阻断结构；FIG. 5 shows a schematic diagram of setting a muffler groove on the flange structure of the present disclosure, wherein a blocking structure is provided between the head and the tail of the muffler groove;

图6示出了图1中的上法兰的剖视图；Figure 6 shows a cross-sectional view of the upper flange in Figure 1;

图7示出了本公开的限位板的示意图；FIG. 7 shows a schematic diagram of the limiting plate of the present disclosure;

图8示出了本公开的法兰结构的中心轴与消音凹槽距离关系的示意图；8 is a schematic diagram showing the relationship between the distance between the central axis of the flange structure of the present disclosure and the muffler groove;

图9示出了本公开的法兰结构上开设消音凹槽的结构图，其中限位板排气孔和法兰排气孔分别位于阻断结构的两侧；Fig. 9 shows the structure diagram of opening the muffler groove on the flange structure of the present disclosure, wherein the limit plate exhaust hole and the flange exhaust hole are respectively located on both sides of the blocking structure;

图10示出了本公开的法兰结构上开设消音凹槽的结构图，其中限位板排气孔和法兰排气孔位于阻断结构的同一侧；Figure 10 shows a structural diagram of the flange structure of the present disclosure with a muffler groove, wherein the limit plate exhaust hole and the flange exhaust hole are located on the same side of the blocking structure;

图11示出了本公开的法兰结构上开设消音凹槽的结构图，其中限位板排气孔和法兰排气孔位于阻断结构的两侧，且阻断结构相对于图9而言更厚；FIG. 11 shows a structural diagram of the flange structure of the present disclosure with a muffler groove, wherein the limit plate exhaust hole and the flange exhaust hole are located on both sides of the blocking structure, and the blocking structure is different from FIG. 9 . speak thicker

图12示出了本公开的法兰结构的端面上开设微孔结构的示意图；12 shows a schematic diagram of opening a microporous structure on the end face of the flange structure of the present disclosure;

图13示出了本公开的法兰结构上开设消音凹槽的示意图；FIG. 13 shows a schematic diagram of opening a muffler groove on the flange structure of the present disclosure;

图14示出了图13中的法兰结构的侧壁上开设微孔结构的示意图；Figure 14 shows a schematic diagram of opening a microporous structure on the side wall of the flange structure in Figure 13;

图15示出了本公开的法兰结构中窄区域处的过流通道截面积S的示意图；FIG. 15 shows a schematic diagram of the cross-sectional area S of the flow passage at the narrow region in the flange structure of the present disclosure;

图16示出了本公开中排气孔组的一个实施方式的示意图；Figure 16 shows a schematic diagram of one embodiment of a vent set of the present disclosure;

图17示出了本公开中排气孔组的另一个实施方式的示意图；FIG. 17 shows a schematic diagram of another embodiment of a vent group of the present disclosure;

图18示出了本公开中排气孔组的另一个实施方式的示意图；Figure 18 shows a schematic diagram of another embodiment of a vent set of the present disclosure;

图19示出了本公开中排气孔组的另一个实施方式的示意图；Figure 19 shows a schematic diagram of another embodiment of a vent set of the present disclosure;

图20示出了本公开中排气孔组的另一个实施方式的示意图；FIG. 20 shows a schematic diagram of another embodiment of a vent set of the present disclosure;

图21示出了本公开中排气孔组的另一个实施方式的示意图；Figure 21 shows a schematic diagram of another embodiment of a vent set of the present disclosure;

图22示出了本公开的法兰结构上设置消音凹槽的示意图，其中消音凹槽首尾间设置阻断结构，且具有六个连接凸台；Fig. 22 shows a schematic diagram of the muffler groove provided on the flange structure of the present disclosure, wherein a blocking structure is arranged between the head and the tail of the muffler groove, and there are six connection bosses;

图23示出了图22中的连接凸台的示意图；Figure 23 shows a schematic diagram of the connection boss in Figure 22;

图24示出了本公开的法兰结构具有三个连接凸台的示意图；Figure 24 shows a schematic diagram of the flange structure of the present disclosure having three connection bosses;

图25示出了本公开的连接凸台处设置三个焊点时的示意图，其中焊点单层设置，其中连接凸台的个数为三个；25 shows a schematic diagram of the present disclosure when three solder joints are arranged at the connection bosses, wherein the solder joints are arranged in a single layer, and the number of the connection bosses is three;

图26示出了图25中连接凸台的示意图；Figure 26 shows a schematic diagram of the connection boss in Figure 25;

图27示出了本公开的连接凸台处设置六个焊点时的示意图，其中连接凸台的个数为六个且焊点单层设置；27 shows a schematic diagram of the present disclosure when six solder joints are arranged at the connection bosses, wherein the number of the connection bosses is six and the solder joints are arranged in a single layer;

图28示出了图27中连接凸台的示意图；Figure 28 shows a schematic diagram of the connection boss in Figure 27;

图29示出了本公开的连接凸台处设置六个焊点的示意图，其中连接凸台的个数为三个且焊点双层设置；Figure 29 shows a schematic diagram of six solder joints disposed at the connection bosses of the present disclosure, wherein the number of the connection bosses is three and the solder joints are double-layered;

图30示出了图29中连接凸台的示意图；Figure 30 shows a schematic diagram of the connection boss in Figure 29;

图31示出了本公开的连接凸台处设置六个焊点的示意图，其中连接凸台的个数为六个、焊点单层设置且第一位置和第二位置交替设置；31 shows a schematic diagram of six solder joints disposed at the connection boss of the present disclosure, wherein the number of the connection boss is six, the solder joints are arranged in a single layer, and the first position and the second position are alternately arranged;

图32示出了图31中连接凸台的示意图；Figure 32 shows a schematic diagram of the connection boss in Figure 31;

图33示出了本公开的连接凸台处设置八个焊点的示意图，其中连接凸台的个数为四个且焊点双层设置；FIG. 33 shows a schematic diagram of eight solder joints disposed at the connection bosses of the present disclosure, wherein the number of the connection bosses is four and the solder joints are arranged in two layers;

图34示出了图33中连接凸台的示意图。FIG. 34 shows a schematic diagram of the connection boss in FIG. 33 .

其中，上述附图包括以下附图标记：Wherein, the above-mentioned drawings include the following reference signs:

10、气缸；20、活塞；30、转轴；40、气缸套；4011、气缸套连通孔；4012、气缸套排气孔；4013、中间腔；50、上法兰；5011、法兰排气孔；5021、阻断结构；5031、消音凹槽；5041、微孔结构；5051、连接凸台；5061、焊点；5071、轴颈；70、上限位板；7011、限位板排气孔。10, cylinder; 20, piston; 30, shaft; 40, cylinder liner; 4011, connecting hole of cylinder liner; 4012, exhaust hole of cylinder liner; 4013, middle cavity; 50, upper flange; 5011, exhaust hole of flange 5021, blocking structure; 5031, muffler groove; 5041, microporous structure; 5051, connecting boss; 5061, solder joint; 5071, journal; 70, upper limit plate; 7011, limit plate exhaust hole.

具体实施方式Detailed ways

需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本公开。It should be noted that the embodiments in the present application and the features of the embodiments may be combined with each other in the case of no conflict. The present disclosure will be described in detail below with reference to the accompanying drawings and in conjunction with embodiments.

需要指出的是，除非另有指明，本申请使用的所有技术和科学术语具有与本申请所属技术领域的普通技术人员通常理解的相同含义。It should be noted that, unless otherwise specified, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs.

在本公开中，在未作相反说明的情况下，使用的方位词如“上、下、顶、底”通常是针对附图所示的方向而言的，或者是针对部件本身在竖直、垂直或重力方向上而言的；同样地，为便于理解和描述，“内、外”是指相对于各部件本身的轮廓的内、外，但上述方位词并不用于限制本公开。In the present disclosure, unless stated to the contrary, directional words such as "upper, lower, top, bottom" are generally used with respect to the directions shown in the drawings, or with respect to the vertical, In terms of vertical or gravitational direction; similarly, for the convenience of understanding and description, "inner and outer" refers to the inner and outer relative to the contour of each component itself, but the above-mentioned orientation words are not used to limit the present disclosure.

为了改善转缸压缩机在运行过程中，法兰结构不具有消音功能，同时法兰结构由于安装不稳定产生振动噪音的问题，本公开提供一种法兰结构、泵体组件和流体机械。In order to improve the problem that the flange structure does not have a noise reduction function during the operation of the rotary cylinder compressor, and the flange structure generates vibration and noise due to unstable installation, the present disclosure provides a flange structure, a pump body assembly and a fluid machine.

其中，流体机械包括下述的泵体组件，其中，下述的法兰结构为下述泵体组件的一部分。具体的，流体机械为压缩机。在一些实施例中，压缩机是转缸压缩机。The fluid machine includes the following pump body assembly, wherein the following flange structure is a part of the following pump body assembly. Specifically, the fluid machine is a compressor. In some embodiments, the compressor is a rotary cylinder compressor.

如图4至图5所示，法兰结构朝向气缸套40的一侧开设有消音通道，消音通道沿法兰结构的周向延伸，法兰结构还包括法兰排气孔5011，法兰排气孔5011与消音通道连通。As shown in FIG. 4 to FIG. 5 , the side of the flange structure facing the cylinder liner 40 is provided with a muffler channel, and the muffler channel extends along the circumferential direction of the flange structure. The flange structure further includes a flange exhaust hole 5011, and the flange row The air hole 5011 communicates with the muffler passage.

具体地，泵体组件产生的高压气体流入到法兰结构的消音通道内，并沿着消音通道周向流动，流动至法兰排气孔5011处，经法兰排气孔5011排出。有效降低了气动声噪，以使法兰结构具有消音功能。Specifically, the high-pressure gas generated by the pump body assembly flows into the muffler channel of the flange structure, flows along the circumferential direction of the muffler channel, flows to the flange exhaust hole 5011 , and is discharged through the flange exhaust hole 5011 . The aerodynamic noise is effectively reduced, so that the flange structure has the function of silencing.

在本公开中，法兰结构上的消音通道可以连通(非阻断式)，也可以不连通(阻断式)，以能使法兰结构通过设置消音通道达到降低噪音的效果为准。In the present disclosure, the silencing channels on the flange structure may be connected (non-blocking type) or not (blocking type), whichever can be achieved by providing the silencing channels on the flange structure to reduce noise.

在图4所示的具体实施例中，消音通道是一个连续的通道，并没有设置阻断结构5021(示出在图5中，图5给出了具有阻断结构的消音通道，需要在后面单独介绍，这里就不赘述了)。In the specific embodiment shown in FIG. 4 , the silencing channel is a continuous channel, and no blocking structure 5021 is provided (shown in FIG. 5 , which shows the silencing channel with blocking structure, which needs to be followed by It is introduced separately and will not be repeated here).

需要说明的是，在如图4所示的具体实施例中，消音通道可以由一个连续的消音凹槽5031构成，也可以由多个消音凹槽5031构成。当消音通道由多个消音凹槽5031构成时，多个消音凹槽5031沿法兰结构的周向间隔设置，且相邻两个消音凹槽5031通过连通孔连通，多个消音凹槽5031配合构成一个消音通道。多个消音凹槽5031的形状可以至少一部分相同，也可以均不相同，由于组合形式较多此处不一一列举。消音凹槽5031设置在法兰结构的侧面，以使泵体组件的高压气流流经消音凹槽5031后排出法兰结构，对高压气体进行消音降噪。It should be noted that, in the specific embodiment shown in FIG. 4 , the muffler channel may be constituted by one continuous muffler groove 5031 , or may be composed of a plurality of muffler grooves 5031 . When the muffler channel is composed of a plurality of muffler grooves 5031, the plurality of muffler grooves 5031 are arranged at intervals along the circumferential direction of the flange structure, and two adjacent muffler grooves 5031 are communicated through communication holes, and the plurality of muffler grooves 5031 cooperate with each other. form a silencer channel. The shapes of the plurality of sound-absorbing grooves 5031 may be at least partially the same, or may be different in all, since there are many combinations, they will not be listed here one by one. The muffler groove 5031 is arranged on the side of the flange structure, so that the high-pressure air flow of the pump body assembly flows through the muffler groove 5031 and then exits the flange structure, so as to muffle and reduce the high pressure gas.

如图4所示，消音凹槽5031的侧壁具有向法兰结构的中心轴突出的筋状结构，筋状结构为多个，多个筋状结构沿消音凹槽5031的侧壁间隔设置，以使消音通道具有交替设置的宽过流区域和窄过流区域。As shown in FIG. 4 , the side wall of the muffler groove 5031 has a rib-like structure protruding toward the central axis of the flange structure, and there are multiple rib-shaped structures, and the plurality of rib-shaped structures are arranged along the side wall of the muffler groove 5031 at intervals. In order to make the muffler channel have alternately arranged wide and narrow over-current regions.

具体地，通过设置在消音通道的侧壁上的多个间隔设置的筋状结构，以使消音通道内部形成具有交替设置的宽过流区域和窄过流区域。当气体流到消音通道内部时，气体经过多个间隔设置的宽过流区域和窄过流区域时进行多次节流、膨胀，以降低噪音。Specifically, a plurality of rib-like structures arranged on the side wall of the muffler passage at intervals are used to form the inside of the muffler passage with alternately arranged wide flow regions and narrow flow regions. When the gas flows into the muffler passage, the gas undergoes multiple throttling and expansion when passing through a plurality of spaced wide flow regions and narrow flow regions to reduce noise.

在本公开中，筋状结构的个数大于3个且小于5个。多个筋状结构使消音通道形成具有交替设置的宽过流区域和窄过流区域，以增加节流、膨胀的次数，需要说明的是，节流和膨胀的次数并不是越多越好，当筋状结构的个数大于3个且小于5个具有降噪消音的功能。在本实施例中，筋状结构的个数为3个。In the present disclosure, the number of tendon structures is greater than 3 and less than 5. Multiple rib-like structures form the muffler channel with alternately arranged wide over-flow areas and narrow over-flow areas to increase the times of throttling and expansion. It should be noted that the more times of throttling and expansion, the better. When the number of tendon structures is more than 3 and less than 5, it has the function of noise reduction and noise reduction. In this embodiment, the number of tendon structures is three.

需要说明的是，各筋状结构与法兰结构的中心轴之间的距离可以是相等。多个筋状结构以法兰结构的中心轴为中心设置在消音通道内部，且距离法兰结构的中心轴相等，以增强消音效果。当然，也不是所有的筋状结构与法兰结构的中心轴之间的距离都必须相等。不同的筋状结构与法兰结构的中心轴之间的距离可以是部分不同，也可以是全部不同的，这里就不一一进行列举了，主要是以能够实现消音功能为基础，合理设置筋状结构与法兰结构的中心轴之间的距离。It should be noted that the distance between each rib-shaped structure and the central axis of the flange structure may be equal. A plurality of tendon structures are arranged inside the muffler channel with the central axis of the flange structure as the center, and are equal to the central axis of the flange structure, so as to enhance the muffler effect. Of course, not all rib-like structures have to be at the same distance from the central axis of the flange structure. The distance between the central axis of the different rib-like structures and the flange structure may be partially different or completely different, which will not be listed here. The distance between the central axis of the flange structure and the flange structure.

如图6所示，法兰结构具有法兰孔，法兰孔与法兰结构的中心轴偏心设置，法兰结构的中部具有轴颈5071，轴颈5071由开设消音通道后的部分构成，法兰孔贯穿轴颈5071的轴向端面，轴颈5071的外周圆与法兰结构的外周圆同轴。As shown in Figure 6, the flange structure has a flange hole, the flange hole and the central axis of the flange structure are eccentrically arranged, the middle of the flange structure has a journal 5071, and the journal 5071 is composed of the part after the noise reduction channel is opened. The flange hole runs through the axial end face of the journal 5071, and the outer circumference of the journal 5071 is coaxial with the outer circumference of the flange structure.

具体地，轴颈5071具有柔性支撑的作用，可减小集中应力，减小法兰结构的磨损，提高法兰结构的稳定性。Specifically, the journal 5071 has the function of flexible support, which can reduce the concentrated stress, reduce the wear of the flange structure, and improve the stability of the flange structure.

如图6所示，轴颈5071背离气缸套40的一侧具有突出于法兰结构的端面的凸环结构，以使法兰结构的轴向上的总高度H大于法兰结构的轴向上的两端面之间的高度H1，消音通道在法兰结构的轴向上的高度H2小于法兰结构的轴向上的两端面之间的高度H1。As shown in FIG. 6 , the side of the journal 5071 facing away from the cylinder liner 40 has a convex ring structure protruding from the end face of the flange structure, so that the total height H of the flange structure in the axial direction is greater than the axial direction of the flange structure The height H1 between the two end faces of the silencing channel in the axial direction of the flange structure H2 is smaller than the height H1 between the two end faces of the flange structure in the axial direction.

具体地，当法兰结构的轴向上的高度H2大于H1时，此时消音通道的深度足够大，以保证进入到消音通道内部的气体能够在消音通道内流动并降低噪音。当法兰结构的轴向上的高度H2小于H1时，此时消音通道的深度过小无法有效实现降噪的效果。Specifically, when the height H2 of the flange structure in the axial direction is greater than H1, the depth of the muffler passage is large enough to ensure that the gas entering the muffler passage can flow in the muffler passage and reduce noise. When the height H2 in the axial direction of the flange structure is less than H1, the depth of the muffler channel is too small to effectively achieve the effect of noise reduction.

需要说明的是，0.5H<H1<0.9H，0.3H<H2<0.7H。当法兰结构的轴向上的两端面之间的高度H1和法兰结构的轴向上的高度H2分别于法兰结构的轴向上的总高度H的大小关系保持在上述范围内，可有效降低噪音且可减小集中应力，减小磨损提高稳定性。It should be noted that 0.5H<H1<0.9H, 0.3H<H2<0.7H. When the relationship between the height H1 between the two end faces in the axial direction of the flange structure and the height H2 in the axial direction of the flange structure and the total height H in the axial direction of the flange structure is maintained within the above range, it can be Effectively reduce noise, reduce concentrated stress, reduce wear and improve stability.

如图6所示，法兰结构的侧壁厚度L1、法兰结构的端面厚度L2满足如下的关系：0.05H<L1<0.25H；0.1H<L2<0.4H。As shown in Figure 6, the thickness L1 of the side wall of the flange structure and the thickness L2 of the end face of the flange structure satisfy the following relationship: 0.05H<L1<0.25H; 0.1H<L2<0.4H.

具体地，法兰结构的侧壁厚度L1过小时，影响法兰结构的刚度，法兰结构的侧壁厚度L1过大时，影响消音效果；法兰结构的端面厚度L2过小时，影响法兰结构的刚度，法兰结构的端面厚度L2过大时，影响消音效果，合理的端面厚度可以保证消音效果。Specifically, if the side wall thickness L1 of the flange structure is too small, the stiffness of the flange structure will be affected; if the side wall thickness L1 of the flange structure is too large, the noise reduction effect will be affected; if the end face thickness L2 of the flange structure is too small, the flange structure will be affected. When the rigidity of the structure and the end face thickness L2 of the flange structure are too large, the noise reduction effect will be affected. A reasonable end face thickness can ensure the noise reduction effect.

如图6和图8所示，消音通道的侧壁具有向法兰结构的中心轴突出的筋状结构，轴颈的轴向端面的最小厚度L3与筋状结构至轴颈的中心k2之间的距离R3之间的关系为0.05H<L3<R3。As shown in Figures 6 and 8, the side wall of the muffler channel has a rib-like structure protruding toward the central axis of the flange structure, and the minimum thickness L3 of the axial end face of the journal is between the rib-like structure and the center k2 of the journal. The relationship between the distance R3 is 0.05H<L3<R3.

具体地，筋状结构影响高压气体的节流膨胀，合理的轴颈5071的轴向端面的最小厚度与筋状结构至法兰结构的中心轴之间的距离R3，可以保证法兰结构刚度的同时，加强降噪效果。Specifically, the rib-shaped structure affects the throttling and expansion of the high-pressure gas. A reasonable minimum thickness of the axial end face of the journal 5071 and the distance R3 between the rib-shaped structure and the central axis of the flange structure can ensure the rigidity of the flange structure. At the same time, the noise reduction effect is enhanced.

如图8所示，法兰结构的中部具有轴颈，轴颈的中心k2与法兰结构的法兰轴孔中心k1之间具有偏心量e，法兰结构的法兰轴孔中心k1与消音凹槽的外侧槽壁之间的距离为R1，筋状结构至轴颈的中心k2的距离为R3，由轴颈的中心k2至消音凹槽的内侧槽壁之间的距离为R2，且R1、R2、R3之间满足如下关系：0.1<(R1-R2)/(R3-R2)<0.4。在本实施例中，0.15<(R1-R2)/(R3-R2)<0.25。As shown in Figure 8, there is a journal in the middle of the flange structure, and there is an eccentricity e between the center k2 of the journal and the center k1 of the flange shaft hole of the flange structure. The distance between the outer groove walls of the groove is R1, the distance from the tendon structure to the center k2 of the journal is R3, the distance from the center k2 of the journal to the inner groove wall of the muffler groove is R2, and R1 , R2 and R3 satisfy the following relationship: 0.1<(R1-R2)/(R3-R2)<0.4. In this embodiment, 0.15<(R1-R2)/(R3-R2)<0.25.

需要说明的是，本公开中的法兰结构为上法兰50。It should be noted that the flange structure in the present disclosure is the upper flange 50 .

如图8所示，各宽过流区域处的距离R1均相等，以构成参考第一参考圆；各窄过流区域处的距离R3均相等，以构成参考第二参考圆；各宽过流区域和窄过流区域处的距离R2均相等，以构成参考第三参考圆。As shown in Figure 8, the distances R1 at each wide overcurrent area are equal to form the first reference circle; the distances R3 at each narrow overcurrent area are equal to form the second reference circle; The distance R2 at both the area and the narrow overcurrent area is equal to form a reference third reference circle.

如图1至图3所示，泵体组件还包括转轴30、限位板和气缸套40，限位板具有限位板排气孔7011，气缸套40具有气缸套排气孔4012，转轴30依次穿过法兰结构、限位板和气缸套40，气缸套排气孔4012、限位板排气孔7011和法兰结构的消音通道连通。在本实施例中，限位板为上限位板70。As shown in FIGS. 1 to 3 , the pump body assembly further includes a rotating shaft 30 , a limit plate and a cylinder liner 40 , the limit plate has a limit plate exhaust hole 7011 , the cylinder liner 40 has a cylinder liner exhaust hole 4012 , and the rotating shaft 30 Passing through the flange structure, the limiting plate and the cylinder liner 40 in sequence, the exhaust hole 4012 of the cylinder liner, the exhaust hole 7011 of the limiting plate and the muffler channel of the flange structure are communicated. In this embodiment, the limiting plate is the upper limiting plate 70 .

当然，若设计的泵体组件是下排气结构时，法兰结构可以为下法兰，限位板可以为下限位板。Of course, if the designed pump body assembly is the lower exhaust structure, the flange structure can be the lower flange, and the limit plate can be the lower limit plate.

具体地，气体依次流经气缸套排气孔4012、限位板排气孔7011进入到法兰结构的消音通道，在消音通道内经过多次节流膨胀以达到降噪消音的效果，然后经过法兰排气孔5011排出。Specifically, the gas flows through the exhaust hole 4012 of the cylinder liner and the exhaust hole 7011 of the limit plate in turn to enter the muffler channel of the flange structure, and undergoes multiple throttling and expansion in the muffler channel to achieve the effect of noise reduction and noise reduction, and then passes through the muffler channel. Flange exhaust hole 5011 is exhausted.

限位板排气孔7011与法兰结构的法兰排气孔5011在法兰结构的周向上间隔设置。图4和图5中，限位板排气孔7011与法兰结构的法兰排气孔5011错开，可以使得由限位板排气孔7011进入的高压气体不会直接由法兰排气孔5011排走，而是在消音通道内部流动一定的距离后，在消音通道内经过多次节流膨胀以达到降噪消音的效果，然后经过法兰排气孔5011排出。The limit plate exhaust hole 7011 and the flange exhaust hole 5011 of the flange structure are arranged at intervals in the circumferential direction of the flange structure. In Figs. 4 and 5, the limit plate exhaust hole 7011 is staggered from the flange exhaust hole 5011 of the flange structure, so that the high-pressure gas entering through the limit plate exhaust hole 7011 will not directly pass through the flange exhaust hole. 5011 is exhausted, but after flowing for a certain distance inside the muffler channel, it undergoes multiple throttling and expansion in the muffler channel to achieve the effect of noise reduction and noise reduction, and then it is discharged through the flange exhaust hole 5011.

需要说明的是，根据阻断结构5021设置的位置和角度的不同，法兰结构的消音通道具有多个不同的结构，由于阻断结构5021可以是多个不同的角度，也可以设置在消音通道的任一位置，因此不对阻断结构5021不同位置和角度的组合的具体实施方式一一列举。It should be noted that, according to the different positions and angles of the blocking structure 5021, the muffler channel of the flange structure has a number of different structures. Since the blocking structure 5021 can be at multiple different angles, it can also be arranged in the muffler channel. Therefore, the specific embodiments of the combination of different positions and angles of the blocking structure 5021 are not listed one by one.

如图1至图3所示，在本公开中气缸套排气孔4012为多个，气缸套40具有多个中间腔4013，各中间腔4013均通过对应的气缸套排气孔4012与气缸套40的容积腔连通，气缸套40还具有与各中间腔4013连通的多个气缸套连通孔4011，限位板排气孔7011为多个，多个气缸套连通孔4011与多个限位板排气孔7011一一对应设置。As shown in FIGS. 1 to 3 , in the present disclosure, there are multiple cylinder liner exhaust holes 4012 , and the cylinder liner 40 has multiple intermediate cavities 4013 , each intermediate cavity 4013 passes through the corresponding cylinder liner exhaust hole 4012 and the cylinder liner. 40 is connected to the volume cavity, the cylinder liner 40 also has a plurality of cylinder liner communication holes 4011 that communicate with each intermediate cavity 4013, a plurality of limit plate exhaust holes 7011, a plurality of cylinder liner communication holes 4011 and a plurality of limit plates The exhaust holes 7011 are arranged in a one-to-one correspondence.

具体地，在气缸套40内部设置多个气缸套排气孔4012和多个中间腔4013，多个气缸套排气孔4012可增加排气效率，多个气缸套排气孔4012将容积腔内部的气体排入到中间腔4013内部，中间腔4013具有缓冲的作用，然后中间腔4013内部的气体依次经过多个气缸套连通孔4011、多个限位板排气孔7011排入到消音通道内部。多个气缸套排气孔4012加快了气体的排出，同时多个中间腔4013具有缓冲气体的作用。Specifically, a plurality of cylinder liner exhaust holes 4012 and a plurality of intermediate cavities 4013 are arranged inside the cylinder liner 40. The multiple cylinder liner exhaust holes 4012 can increase the exhaust efficiency, and the plurality of cylinder liner exhaust holes 4012 can reduce the volume inside the cavity. The gas in the middle cavity 4013 is discharged into the middle cavity 4013, and the middle cavity 4013 has the function of buffering, and then the gas in the middle cavity 4013 is discharged into the muffler channel through the plurality of cylinder liner communication holes 4011 and the plurality of limit plate exhaust holes 7011 in turn. . The plurality of cylinder liner exhaust holes 4012 speed up the discharge of gas, while the plurality of intermediate cavities 4013 have the function of buffering gas.

在一些实施例中，至少两个限位板排气孔7011的大小不同，多个气缸套排气孔4012中的至少两个气缸套排气孔4012的大小不同，各中间腔4013彼此不连通，多个气缸套连通孔4011的至少两个气缸套连通孔4011的大小不同。In some embodiments, the size of at least two limit plate exhaust holes 7011 is different, the size of at least two cylinder liner exhaust holes 4012 in the plurality of cylinder liner exhaust holes 4012 is different, and the intermediate cavities 4013 are not communicated with each other , at least two cylinder liner communication holes 4011 of the plurality of cylinder liner communication holes 4011 have different sizes.

当然，两个中间腔4013也可以是连通的，这样可以增加气体的流动路径，具体可以根据需要进行合理的设置。Of course, the two intermediate cavities 4013 can also be communicated, which can increase the flow path of the gas, and can be set reasonably according to needs.

在图3、图4和图7所示的具体实施例中，气缸套排气孔4012为两个，且一大一小，小的气缸套排气孔4012也可以成为泄压孔。因为气缸套排气孔4012需要与限位板排气孔7011一一对应，因此两个限位板排气孔7011也是一大一小。In the specific embodiment shown in FIG. 3 , FIG. 4 and FIG. 7 , there are two cylinder liner exhaust holes 4012 , one large and one small, and the small cylinder liner exhaust hole 4012 can also be a pressure relief hole. Because the cylinder liner exhaust holes 4012 need to correspond one-to-one with the limit plate exhaust holes 7011 , the two limit plate exhaust holes 7011 are also one large and one small.

具体地，限位板排气孔7011为两个并包括孔径不同的大孔和小孔。其中，小孔与法兰排气孔5011在法兰结构的周向上角度大于160度且小于200度，同时大孔相对于小孔设置在远离法兰排气孔5011的位置，以加强降噪消音的效果。Specifically, the limit plate exhaust holes 7011 are two and include large holes and small holes with different diameters. Among them, the angle between the small hole and the flange exhaust hole 5011 in the circumferential direction of the flange structure is greater than 160 degrees and less than 200 degrees, and the large hole is arranged at a position far from the flange exhaust hole 5011 relative to the small hole to enhance noise reduction. Noise-cancelling effect.

如图4所示，限位板排气孔7011与法兰结构的法兰排气孔5011在法兰结构的周向上间隔设置。As shown in FIG. 4 , the exhaust holes 7011 of the limiting plate and the flange exhaust holes 5011 of the flange structure are arranged at intervals in the circumferential direction of the flange structure.

具体地，限位板排气孔7011和法兰排气孔5011周向上间隔设置，当气体流经限位板排气孔7011进入到消音通道内部时，气体由限位板排气孔7011流动到法兰排气孔5011处，然后经法兰排气孔5011排出。此时气体可在消音通道内部进行多次的节流膨胀，以进行降噪消音。Specifically, the limit plate exhaust hole 7011 and the flange exhaust hole 5011 are arranged at intervals in the circumferential direction. When the gas flows through the limit plate exhaust hole 7011 and enters the interior of the muffler passage, the gas flows through the limit plate exhaust hole 7011 To the flange exhaust hole 5011, and then exhaust through the flange exhaust hole 5011. At this time, the gas can be throttled and expanded many times inside the muffler channel to reduce noise and muffle.

如图1至图2所示，在本公开中，泵体组件还包括气缸10和活塞20，气缸10可转动地设置在气缸套40的容积腔内，气缸10上沿其径向开设有活塞20孔，活塞20具有滑移孔，转轴30的至少一部分穿设在滑移孔内，活塞20随转轴30转动的过程中，活塞20相对于转轴30在活塞20孔内滑动，且气缸10同步转动。As shown in FIGS. 1 to 2 , in the present disclosure, the pump body assembly further includes a cylinder 10 and a piston 20 , the cylinder 10 is rotatably arranged in the volume cavity of the cylinder liner 40 , and the cylinder 10 is provided with a piston along its radial direction. 20 hole, the piston 20 has a sliding hole, and at least a part of the rotating shaft 30 is penetrated in the sliding hole. During the rotation of the piston 20 with the rotating shaft 30, the piston 20 slides in the hole of the piston 20 relative to the rotating shaft 30, and the cylinder 10 is synchronized turn.

从以上的描述中，可以看出，本公开上述的实施例实现了如下技术效果：From the above description, it can be seen that the above-mentioned embodiments of the present disclosure achieve the following technical effects:

通过在法兰结构的一侧设置周向延伸的消音通道，以使现法兰结构具有消音功能，周向延伸的消音通道增大了气体的流动路径，有效减小了气体流动的噪音。现有技术中的转缸压缩机需要与消音器配合使用以进行降噪消音，现有的转缸压缩机的法兰结构不具有消音功能。By arranging a circumferentially extending sound-absorbing channel on one side of the flange structure, the existing flange structure has a sound-absorbing function, and the circumferentially extending sound-absorbing channel increases the flow path of the gas and effectively reduces the noise of the gas flow. The rotary cylinder compressor in the prior art needs to be used in conjunction with a muffler for noise reduction and noise reduction, and the flange structure of the existing rotary cylinder compressor does not have a noise reduction function.

为了改善现有的转缸压缩机在运行过程中，法兰结构不具有消音功能的问题，可以通过在法兰结构上开设不连通的消音凹槽(阻断式，可以参考图5示出的结构)以优化法兰结构达到实现法兰结构具有消音功能，降低气动声噪。In order to improve the problem that the flange structure does not have a sound-absorbing function during the operation of the existing rotary-cylinder compressor, a disconnected sound-absorbing groove (blocking type, can refer to Fig. 5) can be opened on the flange structure. structure) to optimize the flange structure to achieve the flange structure with a noise reduction function and reduce aerodynamic noise.

具体地，当消音通道不连通时，参考图5所示的方式，消音通道的首尾之间形成阻断结构5021，以能使进入到消音通道内部的气体沿定向路径流动，可以增强降噪效果，同时阻断结构5021可增加法兰结构的刚度，提高法兰结构的稳定性。Specifically, when the muffler channel is not connected, referring to the method shown in FIG. 5 , a blocking structure 5021 is formed between the head and the tail of the muffler channel, so that the gas entering the muffler channel can flow along a directional path, which can enhance the noise reduction effect. At the same time, the blocking structure 5021 can increase the rigidity of the flange structure and improve the stability of the flange structure.

具体地，如图9至图10所示，法兰结构朝向气缸套40的一侧开设有消音凹槽5031，消音凹槽5031沿法兰结构的周向延伸且首尾不连通，以在消音凹槽5031的首尾之间形成阻断结构5021，法兰结构还包括法兰排气孔5011，法兰排气孔5011与消音凹槽5031连通且位于消音凹槽5031的一端。Specifically, as shown in FIG. 9 to FIG. 10 , the side of the flange structure facing the cylinder liner 40 is provided with a muffler groove 5031, and the muffler groove 5031 extends along the circumferential direction of the flange structure and is not connected end to end, so that the muffler groove 5031 is not connected to the end of the muffler groove A blocking structure 5021 is formed between the head and tail of the groove 5031 , and the flange structure further includes a flange exhaust hole 5011 . The flange exhaust hole 5011 communicates with the muffler groove 5031 and is located at one end of the muffler groove 5031 .

通过在法兰结构的一侧开设消音凹槽5031，以增加高压气体的流通路径，降低噪音，同时增加了法兰结构的刚度，提高了法兰结构的稳定性。通过将法兰结构与消音器一体设计，在转缸压缩机的泵体组件实际运行的过程中，进入消音凹槽内的高压气体在流经消音凹槽规划的消音路径后，能够经法兰排气孔排出，从而完成消音和排气一体化的过程。By opening a muffler groove 5031 on one side of the flange structure, the flow path of the high-pressure gas is increased, the noise is reduced, the rigidity of the flange structure is increased, and the stability of the flange structure is improved. By integrating the flange structure with the muffler, during the actual operation of the pump body assembly of the rotary compressor, the high-pressure gas entering the muffler groove can pass through the flange after flowing through the muffler path planned by the muffler groove. The exhaust hole is exhausted to complete the process of integrating muffler and exhaust.

具体地，在法兰结构的一侧开设消音凹槽5031，法兰结构上的法兰排气孔5011与消音凹槽5031连通且位于消音凹槽5031的一端。在一些实施例中，消音凹槽5031沿法兰结构的周向延伸且首尾不连通，以在消音凹槽5031的首尾之间形成阻断结构5021。气体经法兰结构进入到消音凹槽5031内部，在消音凹槽5031内设置阻断结构5021使气体在消音凹槽5031内沿一个方向流通，可增加气体在消音凹槽5031内部的流通路径，气体在流通路径内节流膨胀后从消音凹槽5031的法兰排气孔5011排出，有效减少噪音。同时阻断结构5021具有良好的支撑作用，加强了法兰结构的刚度，在泵体组件运行的过程，法兰结构更加稳定。Specifically, a muffler groove 5031 is provided on one side of the flange structure, and the flange exhaust hole 5011 on the flange structure communicates with the muffler groove 5031 and is located at one end of the muffler groove 5031 . In some embodiments, the muffler grooves 5031 extend along the circumferential direction of the flange structure and are not connected to each other, so as to form a blocking structure 5021 between the head and tail of the muffler grooves 5031 . The gas enters the muffler groove 5031 through the flange structure, and the blocking structure 5021 is arranged in the muffler groove 5031 to make the gas flow in one direction in the muffler groove 5031, which can increase the flow path of the gas in the muffler groove 5031. After the gas is throttled and expanded in the flow path, it is discharged from the flange exhaust hole 5011 of the muffler groove 5031, which effectively reduces noise. At the same time, the blocking structure 5021 has a good supporting effect, which strengthens the rigidity of the flange structure. During the operation of the pump body assembly, the flange structure is more stable.

如图9至图10所示，消音凹槽5031的侧壁具有向法兰结构的中心轴突出的筋状结构，筋状结构为多个，多个筋状结构沿消音凹槽5031的侧壁间隔设置，以使消音凹槽5031具有交替设置的宽过流区域和窄过流区域。As shown in FIG. 9 to FIG. 10 , the side wall of the muffler groove 5031 has a rib-like structure protruding toward the central axis of the flange structure, and there are multiple rib-shaped structures along the side wall of the muffler groove 5031 They are spaced so that the muffler grooves 5031 have alternately arranged wide and narrow flow regions.

具体地，通过设置在消音凹槽5031的侧壁上的多个间隔设置的筋状结构，以使消音凹槽5031内部形成具有交替设置的宽过流区域和窄过流区域。当气体流到消音凹槽5031内部时，气体经过多个间隔设置的宽过流区域和窄过流区域时进行多次节流、膨胀，以降低噪音。Specifically, through a plurality of rib-like structures disposed on the sidewall of the muffler groove 5031 at intervals, the inside of the muffler groove 5031 is formed with alternately arranged wide flow regions and narrow flow regions. When the gas flows into the muffler groove 5031, the gas undergoes multiple throttling and expansion when passing through a plurality of spaced wide flow regions and narrow flow regions to reduce noise.

在本公开中，筋状结构的个数大于1个且小于5个。多个筋状结构使消音凹槽5031形成具有交替设置的宽过流区域和窄过流区域，以增加节流、膨胀的次数，需要说明的是，节流和膨胀的次数并不是越多越好，当筋状结构的个数大于1个且小于5个具有降噪消音的功能。在本实施例中，筋状结构的个数为3个。In the present disclosure, the number of tendon-like structures is greater than one and less than five. Multiple rib-like structures make the muffler groove 5031 form a wide flow area and a narrow flow area alternately arranged to increase the number of throttling and expansion. It should be noted that the more the number of throttling and expansion, the better. Well, when the number of tendon-like structures is greater than 1 and less than 5, it has the function of noise reduction and noise reduction. In this embodiment, the number of tendon structures is three.

如图9至图10所示，各筋状结构与法兰结构的中心轴之间的距离相等。多个筋状结构以法兰结构的中心轴为中心设置在消音凹槽5031内部，且距离法兰结构的中心轴相等，以增强消音效果。当然，也不是所有的筋状结构与法兰结构的中心轴之间的距离都必须相等。不同的筋状结构与法兰结构的中心轴之间的距离可以是部分不同，也可以是全部不同的，这里就不一一进行列举了，主要是以能够实现消音功能为基础，合理设置筋状结构与法兰结构的中心轴之间的距离。As shown in FIG. 9 to FIG. 10 , the distances between each rib-like structure and the central axis of the flange structure are equal. A plurality of rib-like structures are arranged inside the muffler groove 5031 with the central axis of the flange structure as the center, and the distance from the central axis of the flange structure is equal to enhance the muffler effect. Of course, not all rib-like structures have to be at the same distance from the central axis of the flange structure. The distance between the central axis of different rib-like structures and the flange structure may be partially different or completely different, which will not be listed here. The distance between the central axis of the flange structure and the flange structure.

如图9至图10所示，阻断结构5021的厚度D1与法兰结构的侧壁厚度G1之间满足G1≤D1≤6G1。阻断结构5021的厚度D1具有加强法兰结构刚度的作用。As shown in FIGS. 9 to 10 , the thickness D1 of the blocking structure 5021 and the thickness G1 of the sidewall of the flange structure satisfy G1≤D1≤6G1. The thickness D1 of the blocking structure 5021 has the effect of enhancing the rigidity of the flange structure.

具体地，当阻断结构5021的厚度D1小于G1时，阻断结构5021的厚度D1过小会影响法兰结构的刚度，导致法兰结构易出现变形的问题。当阻断结构5021的厚度D1大于6G1时，过大的阻断结构5021影响消音凹槽5031的长度，使气体的流通路径变短，影响消音效果。Specifically, when the thickness D1 of the blocking structure 5021 is smaller than G1, if the thickness D1 of the blocking structure 5021 is too small, the rigidity of the flange structure will be affected, and the flange structure may be easily deformed. When the thickness D1 of the blocking structure 5021 is greater than 6G1, the excessively large blocking structure 5021 affects the length of the muffler groove 5031, shortens the gas flow path, and affects the muffler effect.

因此，通过合理的控制阻断结构5021的厚度D1，可以保证消音效果。在图9所示的具体实施例中阻断结构5021的厚度D1相对较小；在图11所示的具体实施例中阻断结构5021的厚度D1相对较厚。Therefore, by reasonably controlling the thickness D1 of the blocking structure 5021, the noise reduction effect can be ensured. In the specific embodiment shown in FIG. 9 , the thickness D1 of the blocking structure 5021 is relatively small; in the specific embodiment shown in FIG. 11 , the thickness D1 of the blocking structure 5021 is relatively thick.

如图9至图10所示，阻断结构5021在消音凹槽5031里具有沿法兰结构的径向延伸的第一阻断面和第二阻断面，以过法兰结构的中心轴的一条直径作为基准线，基准线在法兰结构的周向上与第一阻断面之间具有第一夹角α，基准线在法兰结构的周向上与第二阻断面之间具有第二夹角β，以使第一阻断面和第二阻断面在法兰结构的周向上的夹角为β-α。As shown in FIG. 9 to FIG. 10 , the blocking structure 5021 has a first blocking surface and a second blocking surface extending along the radial direction of the flange structure in the muffler groove 5031 so as to pass through the central axis of the flange structure. A diameter is used as a reference line, the reference line has a first included angle α between the circumferential direction of the flange structure and the first blocking surface, and the reference line has a second angle α between the circumferential direction of the flange structure and the second blocking surface. The included angle β is such that the included angle between the first blocking surface and the second blocking surface in the circumferential direction of the flange structure is β-α.

具体地，阻断结构5021的角度设置在α与β之间，阻断结构5021的角度小于α或者大于β时会影响法兰结构的密封性，具有气体泄漏的风险。Specifically, the angle of the blocking structure 5021 is set between α and β. When the angle of the blocking structure 5021 is smaller than α or larger than β, the sealing performance of the flange structure will be affected, and there is a risk of gas leakage.

如图1至图3所示，泵体组件还包括转轴30、限位板和气缸套40，限位板具有限位板排气孔7011，气缸套40具有气缸套排气孔4012，转轴30依次穿过法兰结构、限位板和气缸套40，气缸套排气孔4012、限位板排气孔7011和法兰结构的消音凹槽5031连通。限位板为上限位板70。As shown in FIGS. 1 to 3 , the pump body assembly further includes a rotating shaft 30 , a limit plate and a cylinder liner 40 , the limit plate has a limit plate exhaust hole 7011 , the cylinder liner 40 has a cylinder liner exhaust hole 4012 , and the rotating shaft 30 Passing through the flange structure, the limit plate and the cylinder liner 40 in sequence, the exhaust hole 4012 of the cylinder liner, the exhaust hole 7011 of the limit plate and the muffler groove 5031 of the flange structure communicate with each other. The limit plate is the upper limit plate 70 .

具体地，气体依次流经气缸套排气孔4012、限位板排气孔7011进入到法兰结构的消音凹槽5031，在消音凹槽5031内经过多次节流膨胀以达到降噪消音的效果，然后经过法兰排气孔5011排出。Specifically, the gas flows sequentially through the exhaust hole 4012 of the cylinder liner and the exhaust hole 7011 of the limit plate into the muffler groove 5031 of the flange structure, and is throttled and expanded for many times in the muffler groove 5031 to achieve noise reduction and noise reduction. effect, and then discharged through the flange exhaust hole 5011.

如图7、图9、图10和图11所示，限位板排气孔7011与法兰结构的法兰排气孔5011在法兰结构的周向上间隔设置。图中，限位板排气孔7011与法兰结构的法兰排气孔5011错开，可以使得由限位板排气孔7011进入的高压气体不会直接由法兰排气孔5011排走，而是在消音凹槽5031内部流动一定的距离后，在消音凹槽5031内经过多次节流膨胀以达到降噪消音的效果，然后经过法兰排气孔5011排出。As shown in FIG. 7 , FIG. 9 , FIG. 10 and FIG. 11 , the exhaust holes 7011 of the limiting plate and the flange exhaust holes 5011 of the flange structure are arranged at intervals in the circumferential direction of the flange structure. In the figure, the limit plate exhaust hole 7011 is staggered from the flange exhaust hole 5011 of the flange structure, so that the high-pressure gas entering through the limit plate exhaust hole 7011 will not be directly exhausted through the flange exhaust hole 5011, Instead, after flowing for a certain distance inside the muffler groove 5031 , the muffler groove 5031 undergoes multiple throttling and expansion to achieve the effect of noise reduction and muffler, and then it is discharged through the flange exhaust hole 5011 .

需要说明的是，如图9至图10所示的具体实施例中，根据阻断结构5021设置的位置和角度的不同，法兰结构的消音凹槽5031具有多个不同的结构，由于阻断结构5021可以是多个不同的角度，也可以设置在消音凹槽5031的任一位置，因此不对阻断结构5021不同位置和角度的组合的具体实施方式一一列举。下面，根据限位板排气孔7011和法兰排气孔5011的分布位置不同提供不同的实施方式。It should be noted that, in the specific embodiments shown in FIG. 9 to FIG. 10 , according to the different positions and angles of the blocking structure 5021 , the muffler groove 5031 of the flange structure has a number of different structures. The structure 5021 can be at a plurality of different angles, and can also be arranged at any position of the muffler groove 5031, so the specific implementations of the combination of different positions and angles of the blocking structure 5021 are not listed one by one. In the following, different embodiments are provided according to the different distribution positions of the vent holes 7011 of the limiting plate and the vent holes 5011 of the flange.

如图9所示的具体实施方式中，限位板排气孔7011和法兰排气孔5011分别位于法兰结构的消音凹槽5031的两端并位于阻断结构5021的两侧。In the specific embodiment shown in FIG. 9 , the limiting plate exhaust hole 7011 and the flange exhaust hole 5011 are respectively located at both ends of the muffler groove 5031 of the flange structure and on both sides of the blocking structure 5021 .

具体地，限位板排气孔7011和法兰排气孔5011分别位于阻断结构5021的两侧，当气体流经限位板排气孔7011进入到消音凹槽5031内部时，气体由消音凹槽5031的一端流动到消音凹槽5031的另一端，然后经法兰排气孔5011排出。此时气体可在消音凹槽5031内部进行多次的节流膨胀，以进行降噪消音。Specifically, the limit plate exhaust hole 7011 and the flange exhaust hole 5011 are located on both sides of the blocking structure 5021, respectively. When the gas flows through the limit plate exhaust hole 7011 and enters the inside of the muffler groove 5031, the gas is removed by the muffler. One end of the groove 5031 flows to the other end of the muffler groove 5031, and then is discharged through the flange exhaust hole 5011. At this time, the gas can be throttled and expanded multiple times in the muffler groove 5031 to perform noise reduction and muffling.

如图10所示的具体实施方式中，限位板排气孔7011和法兰排气孔5011分别位于法兰结构的消音凹槽5031的两端并位于阻断结构5021的同一侧。此时气体需要在消音凹槽5031内经过节流膨胀后经过法兰排气孔5011流出。相比于图9中的方式，图10所提供的流通路径的长度要短一些。In the specific embodiment shown in FIG. 10 , the limiting plate exhaust hole 7011 and the flange exhaust hole 5011 are respectively located at both ends of the muffler groove 5031 of the flange structure and on the same side of the blocking structure 5021 . At this time, the gas needs to be throttled and expanded in the muffler groove 5031 and then flow out through the flange exhaust hole 5011 . Compared to the approach in FIG. 9 , the length of the flow path provided in FIG. 10 is shorter.

如图7和图9所示，限位板排气孔7011为多个，且至少两个限位板排气孔7011的大小不同。多个限位板排气孔7011间隔设置。限位板排气孔7011可以设置多个，以将气体排入到消音凹槽5031内部，为避免过于集中将多个限位板排气孔7011间隔设置。As shown in FIG. 7 and FIG. 9 , there are multiple exhaust holes 7011 in the limiting plate, and at least two exhaust holes 7011 in the limiting plate have different sizes. A plurality of limit plate exhaust holes 7011 are arranged at intervals. A plurality of limit plate exhaust holes 7011 may be provided to discharge gas into the sound-absorbing groove 5031 . To avoid excessive concentration, the plurality of limit plate exhaust holes 7011 are arranged at intervals.

如图7和图9所示，限位板排气孔7011为两个并包括孔径不同的大孔和小孔。其中，小孔与法兰排气孔5011在法兰结构的周向上角度大于30度且小于200度，同时大孔相对于小孔靠近法兰结构的阻断结构5021，以加强降噪消音的效果。As shown in FIG. 7 and FIG. 9 , there are two exhaust holes 7011 in the limiting plate and include large holes and small holes with different diameters. Among them, the angle between the small hole and the flange exhaust hole 5011 in the circumferential direction of the flange structure is greater than 30 degrees and less than 200 degrees, and the large hole is close to the blocking structure 5021 of the flange structure relative to the small hole to enhance noise reduction and noise reduction. Effect.

如图1至图3所示，在本公开中气缸套排气孔4012为多个，气缸套40具有多个中间腔4013，各中间腔4013均通过对应的气缸套排气孔4012与气缸套40的容积腔连通，气缸套40还具有与各中间腔4013连通的多个气缸套连通孔4011，多个气缸套连通孔4011与多个限位板排气孔7011一一对应设置。As shown in FIGS. 1 to 3 , in the present disclosure, there are multiple cylinder liner exhaust holes 4012 , and the cylinder liner 40 has multiple intermediate cavities 4013 , each intermediate cavity 4013 passes through the corresponding cylinder liner exhaust hole 4012 and the cylinder liner. The cylinder liner 40 also has a plurality of cylinder liner communication holes 4011 that communicate with each intermediate cavity 4013, and the plurality of cylinder liner communication holes 4011 are provided in a one-to-one correspondence with a plurality of limit plate exhaust holes 7011.

具体地，在气缸套40内部设置多个气缸套排气孔4012和多个中间腔4013，多个气缸套排气孔4012可增加排气效率，多个气缸套排气孔4012将容积腔内部的气体排入到中间腔4013内部，中间腔4013具有缓冲的作用，然后中间腔4013内部的气体依次经过多个气缸套连通孔4011、多个限位板排气孔7011排入到消音凹槽5031内部。多个气缸套排气孔4012加快了气体的排出，同时多个中间腔4013具有缓冲气体的作用。Specifically, a plurality of cylinder liner exhaust holes 4012 and a plurality of intermediate cavities 4013 are arranged inside the cylinder liner 40. The multiple cylinder liner exhaust holes 4012 can increase the exhaust efficiency, and the plurality of cylinder liner exhaust holes 4012 can reduce the volume inside the cavity. The gas inside the middle cavity 4013 is discharged into the middle cavity 4013, and the middle cavity 4013 has the function of buffering, and then the gas inside the middle cavity 4013 is discharged into the muffler groove through the plurality of cylinder liner communication holes 4011 and the plurality of limit plate exhaust holes 7011 in turn. Inside 5031. The plurality of cylinder liner exhaust holes 4012 speed up the discharge of gas, while the plurality of intermediate cavities 4013 have the function of buffering gas.

在一些实施例中，多个气缸套排气孔4012中的至少两个气缸套排气孔4012的大小不同。各中间腔4013彼此不连通。多个气缸套连通孔4011的至少两个气缸套连通孔4011的大小不同。In some embodiments, at least two cylinder liner exhaust holes 4012 of the plurality of cylinder liner exhaust holes 4012 are of different sizes. The intermediate cavities 4013 do not communicate with each other. At least two cylinder liner communication holes 4011 of the plurality of cylinder liner communication holes 4011 have different sizes.

在图3所示的具体实施例中，气缸套排气孔4012为两个，且一大一小，小的气缸套排气孔4012也可以成为泄压孔。因为气缸套连通孔4011需要与限位板排气孔7011一一对应，因此两个气缸套连通孔4011也是一大一小。In the specific embodiment shown in FIG. 3 , there are two cylinder liner exhaust holes 4012 , one large and one small, and the small cylinder liner exhaust holes 4012 can also be used as pressure relief holes. Because the cylinder liner communication holes 4011 need to be in one-to-one correspondence with the limit plate exhaust holes 7011, the two cylinder liner communication holes 4011 are also one large and one small.

如图2所示，在本公开中，泵体组件还包括气缸和活塞20，气缸可转动地设置在气缸套40的容积腔内，气缸上沿其径向开设有活塞孔，活塞20具有滑移孔，转轴30的至少一部分穿设在滑移孔内，活塞20随转轴30转动的过程中，活塞20相对于转轴30在活塞孔内滑动，且气缸同步转动。As shown in FIG. 2 , in the present disclosure, the pump body assembly further includes a cylinder and a piston 20 , the cylinder is rotatably arranged in the volume cavity of the cylinder liner 40 , a piston hole is opened on the cylinder along its radial direction, and the piston 20 has a sliding At least a part of the rotating shaft 30 passes through the sliding hole. During the rotation of the piston 20 with the rotating shaft 30, the piston 20 slides in the piston hole relative to the rotating shaft 30, and the cylinder rotates synchronously.

具体地，在法兰结构的一侧开设消音凹槽5031，法兰结构上的法兰排气孔5011与消音凹槽5031连通且位于消音凹槽5031的一端。在一些实施例中，消音凹槽5031沿法兰结构的周向延伸且首尾不连通，以在消音凹槽5031的首尾之间形成阻断结构5021。气体经法兰结构进入到消音凹槽5031内部，在消音凹槽5031内设置阻断结构5021可增加气体在消音凹槽5031内部的流通路径，气体在流通路径内节流膨胀后从消音凹槽5031的法兰排气孔5011排出，有效减少噪音。同时阻断结构5021具有良好的支撑作用，加强了法兰结构的刚度，在泵体组件运行的过程，法兰结构更加稳定。Specifically, a muffler groove 5031 is provided on one side of the flange structure, and the flange exhaust hole 5011 on the flange structure communicates with the muffler groove 5031 and is located at one end of the muffler groove 5031 . In some embodiments, the muffler grooves 5031 extend along the circumferential direction of the flange structure and are not connected to each other, so as to form a blocking structure 5021 between the head and tail of the muffler grooves 5031 . The gas enters the muffler groove 5031 through the flange structure, and the blocking structure 5021 is arranged in the muffler groove 5031 to increase the flow path of the gas inside the muffler groove 5031. After the gas is throttled and expanded in the flow path, the gas flows from the muffler groove The flange exhaust hole 5011 of 5031 is exhausted, which effectively reduces noise. At the same time, the blocking structure 5021 has a good supporting effect, which strengthens the rigidity of the flange structure. During the operation of the pump body assembly, the flange structure is more stable.

为了改善现有技术中转缸压缩机在运行过程中，法兰结构不具有消音功能的问题，还可以通过在法兰结构上开设排气孔组以优化法兰结构达到实现法兰结构具有消音功能，降低气动声噪。In order to improve the problem that the flange structure does not have the function of silencing during the operation of the transfer cylinder compressor in the prior art, it is also possible to optimize the flange structure by opening an exhaust hole group on the flange structure to achieve the function of the flange structure with silencing. , reduce aerodynamic noise.

具体地，如图1、图2、图3、图7和图12所示，法兰结构朝向气缸套40的一侧开设有消音凹槽5031，消音凹槽5031沿法兰结构的周向延伸，法兰结构具有排气孔组，且排气孔组具有多个微孔结构5041，微孔结构5041位于法兰结构的端面并与消音凹槽5031的槽底连通。Specifically, as shown in FIG. 1 , FIG. 2 , FIG. 3 , FIG. 7 and FIG. 12 , the side of the flange structure facing the cylinder liner 40 is provided with a muffler groove 5031 , and the muffler groove 5031 extends along the circumferential direction of the flange structure , the flange structure has an exhaust hole group, and the exhaust hole group has a plurality of microporous structures 5041. The microporous structures 5041 are located on the end face of the flange structure and communicate with the bottom of the muffler groove 5031.

从以上的描述中，可以看出，通过在法兰结构的一侧开设消音凹槽5031，以增加高压气体的流通路径，在消音凹槽5031内开设微孔结构5041进行排气，消音凹槽5031和微孔结构5041配合使用可以有效提高结构的吸声性，降低噪音。同时微孔结构5041可提高法兰结构的刚度。通过将法兰结构与消音器一体设计，在转缸压缩机的泵体组件实际运行的过程中，进入消音凹槽内的高压气体在流经消音凹槽规划的消音路径后，能够经法兰排气孔排出，从而完成消音和排气一体化的过程。From the above description, it can be seen that by opening a muffler groove 5031 on one side of the flange structure to increase the flow path of high-pressure gas, a microporous structure 5041 is opened in the muffler groove 5031 for exhausting, and the muffler groove The use of 5031 and the microporous structure 5041 can effectively improve the sound absorption of the structure and reduce noise. At the same time, the microporous structure 5041 can improve the rigidity of the flange structure. By integrating the flange structure with the muffler, during the actual operation of the pump body assembly of the rotary compressor, the high-pressure gas entering the muffler groove can pass through the flange after flowing through the muffler path planned by the muffler groove. The exhaust hole is exhausted to complete the process of integrating muffler and exhaust.

相类似的，如图13至图14所示，法兰结构朝向气缸套40的一侧开设有消音凹槽5031，消音凹槽5031沿法兰结构的周向延伸，法兰结构具有排气孔组，且排气孔组具有多个微孔结构5041，微孔结构5041位于法兰结构的侧面并与消音凹槽5031的槽侧壁连通。Similarly, as shown in FIG. 13 to FIG. 14 , the side of the flange structure facing the cylinder liner 40 is provided with a muffler groove 5031, and the muffler groove 5031 extends along the circumferential direction of the flange structure, and the flange structure has an exhaust hole. group, and the exhaust hole group has a plurality of microporous structures 5041, and the microporous structures 5041 are located on the side of the flange structure and communicate with the groove side wall of the muffler groove 5031.

具体地，在法兰结构的一侧开设周向延伸的消音凹槽5031，消音凹槽5031上设置排气孔组。在一些实施例中，排气孔组具有多个微孔结构5041，微孔结构5041与消音凹槽5031槽底连通。气体经法兰结构进入到消音凹槽5031内部，经过多次内节流膨胀后从微孔结构5041排出。消音凹槽5031和微孔结构5041配合使用可以有效提高结构的吸声性，降低噪音。同时微孔结构5041可提高法兰结构的刚度。Specifically, a circumferentially extending muffler groove 5031 is provided on one side of the flange structure, and an exhaust hole group is arranged on the muffler groove 5031 . In some embodiments, the exhaust hole group has a plurality of microporous structures 5041, and the microporous structures 5041 communicate with the bottom of the muffler groove 5031. The gas enters the muffler groove 5031 through the flange structure, and is discharged from the microporous structure 5041 after multiple internal throttling and expansion. The sound-absorbing groove 5031 and the microporous structure 5041 can effectively improve the sound absorption of the structure and reduce the noise. At the same time, the microporous structure 5041 can improve the rigidity of the flange structure.

需要说明的是，法兰结构的端面设置多个微孔结构5041，在转缸压缩机高频率运动的情况下降噪效果不衰减，降噪性能稳定。法兰结构的消音凹槽5031的侧面设置多个微孔结构5041，可以避免高压排气脉冲的直接冲击，有效降低气动噪音。It should be noted that the end face of the flange structure is provided with a plurality of microporous structures 5041, the noise reduction effect is not attenuated and the noise reduction performance is stable under the condition of high frequency motion of the rotary cylinder compressor. A plurality of microporous structures 5041 are arranged on the side of the muffler groove 5031 of the flange structure, which can avoid the direct impact of the high-pressure exhaust pulse and effectively reduce aerodynamic noise.

如图12和图13所示，消音凹槽5031的首尾不连通，以在消音凹槽5031的首尾之间形成阻断结构5021，排气孔组位于消音凹槽5031的一端。当然，消音凹槽5031的首尾也可以是连通的，没有阻断结构的法兰结构的端面或侧面上也可以设置排气孔组。As shown in FIG. 12 and FIG. 13 , the head and tail of the muffler groove 5031 are not connected to form a blocking structure 5021 between the head and the tail of the muffler groove 5031 , and the exhaust hole group is located at one end of the muffler groove 5031 . Of course, the head and tail of the muffler groove 5031 may also be connected, and the exhaust hole group may also be provided on the end face or side face of the flange structure without the blocking structure.

具体地，通过设置阻断结构5021以实现消音凹槽5031首尾不连通的结构，以使气体进入消音凹槽5031内定向流动，同时阻断结构5021具有加强法兰结构刚度的效果，提高法兰结构的稳定性。Specifically, the blocking structure 5021 is provided to realize a structure in which the muffler groove 5031 is not connected to the end, so that the gas enters the muffler groove 5031 to flow directionally, and the blocking structure 5021 has the effect of strengthening the structural rigidity of the flange, improving the flange structure structural stability.

在本公开中，微孔结构5041的孔截面呈圆形、多边形、椭圆形中的一种或多种。具体地，微孔结构5041可以由圆形、多边形、椭圆形中的一种组成，也可以由圆形、多边形、椭圆形中的多种配合组成。微孔结构5041设计可以提高吸声量，降低转缸压缩机运行中的噪音。具体的，多边形可以采用三角形或菱形。In the present disclosure, the cross section of the pores of the microporous structure 5041 is one or more of a circle, a polygon, and an ellipse. Specifically, the microporous structure 5041 may be composed of one of a circle, a polygon, and an ellipse, and may also be composed of a variety of combinations of a circle, a polygon, and an ellipse. The design of the microporous structure 5041 can improve the sound absorption and reduce the noise during the operation of the rotary cylinder compressor. Specifically, the polygon can be a triangle or a rhombus.

需要说明的是，多个微孔结构5041可以构成椭圆形的排气孔组、圆形的排气孔组、多边形的排气孔组、放射状的排气孔组等，由于多个微孔结构5041可构成的排气孔组的形状过多，此处不一一列举。具体可以参考图16至图21所示的几个具体实施方式。It should be noted that a plurality of microporous structures 5041 can form an elliptical vent hole group, a circular vent hole group, a polygonal vent hole group, a radial vent hole group, etc. The shapes of the exhaust hole groups that can be formed by the 5041 are too numerous to be listed here. For details, reference may be made to several specific implementation manners shown in FIG. 16 to FIG. 21 .

本公开中微孔结构5041的孔截面的面积S0小于等于3mm ²。微孔结构5041的孔面积小于等于3mm ²时，微孔结构5041可以有效提高1000HZ以内的低频消声量，有效降低1000HZ以内的噪音。 In the present disclosure, the area S0 of the cross section of the pores of the microporous structure 5041 is less than or equal to 3 mm ² . When the pore area of the microporous structure 5041 is less than or equal to 3 mm ² , the microporous structure 5041 can effectively improve the low-frequency noise reduction within 1000 Hz, and effectively reduce the noise within 1000 Hz.

如图12和图13所示，消音凹槽5031的侧壁具有向法兰结构的中心轴突出的筋状结构，筋状结构为多个，多个筋状结构沿消音凹槽5031的侧壁间隔设置，以使消音凹槽5031具有交替设置的宽过流区域和窄过流区域。As shown in FIG. 12 and FIG. 13 , the side wall of the muffler groove 5031 has a rib-like structure protruding toward the central axis of the flange structure, and there are multiple rib-shaped structures along the side wall of the muffler groove 5031 They are spaced so that the muffler grooves 5031 have alternately arranged wide and narrow flow regions.

在本公开中，如15所示，窄过流区域的过流通道截面积S、微孔结构5041的孔截面的面积S0和微孔结构5041的个数n之间满足：n*S0≤3S。In the present disclosure, as shown in 15, the cross-sectional area S of the flow passage in the narrow flow region, the area S0 of the hole cross-section of the microporous structure 5041, and the number n of the microporous structure 5041 satisfy: n*S0≤3S .

具体地，当满足n*S0≤3S时，气体在宽过流区域和窄过流区域流过时节流膨胀后，经过微孔结构5041排出，可以有效降噪消音。Specifically, when n*S0≤3S is satisfied, the gas is discharged through the microporous structure 5041 after being throttled and expanded when it flows through the wide flow area and the narrow flow area, which can effectively reduce noise.

在本公开中，筋状结构的个数大于2个且小于5个。多个筋状结构使消音凹槽5031形成具有交替设置的宽过流区域和窄过流区域，以增加节流、膨胀的次数，需要说明的是，节流和膨胀的次数并不是越多越好，当筋状结构的个数大于2个且小于5个具有降噪消音的功能。在本实施例中，筋状结构的个数为3个。In the present disclosure, the number of tendon structures is greater than 2 and less than 5. Multiple rib-like structures make the muffler groove 5031 form a wide flow area and a narrow flow area alternately arranged to increase the number of throttling and expansion. It should be noted that the more the number of throttling and expansion, the more Well, when the number of tendon structures is more than 2 and less than 5, it has the function of noise reduction and noise reduction. In this embodiment, the number of tendon structures is three.

需要说明的是，各筋状结构与法兰结构的中心轴之间的距离可以是相等。多个筋状结构以法兰结构的中心轴为中心设置在消音凹槽5031内部，且距离法兰结构的中心轴相等，以增强消音效果。当然，也不是所有的筋状结构与法兰结构的中心轴之间的距离都必须相等。不同的筋状结构与法兰结构的中心轴之间的距离可以是部分不同，也可以是全部不同的，这里就不一一进行列举了，主要是以能够实现消音功能为基础，合理设置筋状结构与法兰结构的中心轴之间的距离。It should be noted that the distance between each rib-shaped structure and the central axis of the flange structure may be equal. A plurality of rib-like structures are arranged inside the muffler groove 5031 with the central axis of the flange structure as the center, and the distance from the central axis of the flange structure is equal to enhance the muffler effect. Of course, not all rib-like structures have to be at the same distance from the central axis of the flange structure. The distance between the central axis of different rib-like structures and the flange structure may be partially different or completely different, which will not be listed here. The distance between the central axis of the flange structure and the flange structure.

如图1至图3和图12所示，泵体组件还包括转轴30、限位板和气缸套40，限位板具有限位板排气孔7011，气缸套40具有气缸套排气孔4012，转轴30依次穿过法兰结构、限位板和气缸套40，气缸套排气孔4012、限位板排气孔7011和法兰结构的消音凹槽5031连通。在本实施例中，限位板为上限位板70。As shown in FIGS. 1 to 3 and 12 , the pump body assembly further includes a rotating shaft 30 , a limit plate and a cylinder liner 40 , the limit plate has a limit plate exhaust hole 7011 , and the cylinder liner 40 has a cylinder liner exhaust hole 4012 , the rotating shaft 30 passes through the flange structure, the limit plate and the cylinder liner 40 in sequence, the cylinder liner exhaust hole 4012, the limit plate exhaust hole 7011 and the muffler groove 5031 of the flange structure communicate with each other. In this embodiment, the limiting plate is the upper limiting plate 70 .

具体地，气体依次流经气缸套排气孔4012、限位板排气孔7011进入到法兰结构的消音凹槽5031，在消音凹槽5031内经过多次节流膨胀以达到降噪消音的效果，然后经过微孔结构5041排出。Specifically, the gas flows sequentially through the exhaust hole 4012 of the cylinder liner and the exhaust hole 7011 of the limit plate into the muffler groove 5031 of the flange structure, and is throttled and expanded for many times in the muffler groove 5031 to achieve noise reduction and noise reduction. effect, and then discharged through the microporous structure 5041.

如图7、图12、图13所示，限位板排气孔7011与法兰结构的排气孔组在法兰结构的周向上间隔设置。图中，限位板排气孔7011与法兰结构的排气孔组错开，可以使得由限位板排气孔7011进入的高压气体不会直接由排气孔组排走，而是在消音凹槽5031内部流动一定的距离后，在消音凹槽5031内经过多次节流膨胀以达到降噪消音的效果，然后经过排气孔组排出。As shown in FIG. 7 , FIG. 12 , and FIG. 13 , the exhaust hole 7011 of the limiting plate and the exhaust hole group of the flange structure are arranged at intervals in the circumferential direction of the flange structure. In the figure, the limit plate exhaust hole 7011 is staggered from the exhaust hole group of the flange structure, so that the high-pressure gas entering through the limit plate exhaust hole 7011 will not be directly exhausted by the exhaust hole group, but will be muffled. After the inside of the groove 5031 flows for a certain distance, it undergoes multiple throttling and expansion in the muffler groove 5031 to achieve the effect of noise reduction and muffler, and then it is discharged through the exhaust hole group.

需要说明的是，根据阻断结构5021设置的位置和角度的不同，法兰结构的消音凹槽5031具有多个不同的结构，由于阻断结构5021可以是多个不同的角度，也可以设置在消音凹槽5031的任一位置，因此不对阻断结构5021不同位置和角度的组合的具体实施方式一一列举。It should be noted that, according to the different positions and angles of the blocking structure 5021, the muffler groove 5031 of the flange structure has a number of different structures. Any position of the muffler groove 5031 is not listed one by one for specific implementations of combinations of different positions and angles of the blocking structure 5021 .

如图3、图12、图13、图14所示，气缸套排气孔4012的直径E与法兰结构的微孔结构5041的直径D之间满足：D≤E≤16D。As shown in FIG. 3 , FIG. 12 , FIG. 13 , and FIG. 14 , the diameter E of the exhaust hole 4012 of the cylinder liner and the diameter D of the microporous structure 5041 of the flange structure satisfy: D≤E≤16D.

具体地，当微孔结构5041的直径D满足D≤E≤16D时，可保证气缸套排气孔4012内排出而气体经过微孔结构5041排出上法兰50时，微孔结构5041可以有效提高吸声量，以降低泵体组件运行过程总的噪音。Specifically, when the diameter D of the microporous structure 5041 satisfies D≤E≤16D, it can be ensured that when the gas is discharged from the exhaust hole 4012 of the cylinder liner and the gas is discharged from the upper flange 50 through the microporous structure 5041, the microporous structure 5041 can effectively improve the The amount of sound absorption to reduce the total noise during the operation of the pump body assembly.

在一些实施例中，至少两个限位板排气孔7011的大小不同。多个气缸套排气孔4012中的至少两个气缸套排气孔4012的大小不同。各中间腔4013彼此不连通。多个气缸套连通孔4011的至少两个气缸套连通孔4011的大小不同。In some embodiments, the size of the at least two limiting plate vent holes 7011 is different. At least two cylinder liner exhaust holes 4012 of the plurality of cylinder liner exhaust holes 4012 are of different sizes. The intermediate cavities 4013 do not communicate with each other. At least two cylinder liner communication holes 4011 of the plurality of cylinder liner communication holes 4011 have different sizes.

如图7、图12、图13所示，限位板排气孔7011与法兰结构的排气孔组分别位于法兰结构的消音凹槽5031的两端并位于法兰结构的阻断结构5021的两侧。As shown in Fig. 7, Fig. 12, Fig. 13, the limit plate exhaust hole 7011 and the exhaust hole group of the flange structure are respectively located at both ends of the muffler groove 5031 of the flange structure and are located in the blocking structure of the flange structure Both sides of the 5021.

具体地，限位板排气孔7011和排气孔组分别位于阻断结构5021的两侧，当气体流经限位板排气孔7011进入到消音凹槽5031内部时，气体由消音凹槽5031的一端流动到消音凹槽5031的另一端，然后经排气孔组排出。此时气体可在消音凹槽5031内部进行多次的节流膨胀，以进行降噪消音。Specifically, the limit plate exhaust hole 7011 and the exhaust hole group are located on both sides of the blocking structure 5021, respectively. When the gas flows through the limit plate exhaust hole 7011 and enters the inside of the muffler groove 5031, the gas is discharged from the muffler groove 5031. One end of 5031 flows to the other end of the muffler groove 5031, and then is discharged through the exhaust hole group. At this time, the gas can be throttled and expanded multiple times in the muffler groove 5031 to perform noise reduction and muffling.

如图1至图2所示，在本公开中，泵体组件还包括气缸和活塞20，气缸可转动地设置在气缸套40的容积腔内，气缸上沿其径向开设有活塞孔，活塞20具有滑移孔，转轴30的至少一部分穿设在滑移孔内，活塞20随转轴30转动的过程中，活塞20相对于转轴30在活塞孔内滑动，且气缸同步转动。As shown in FIGS. 1 to 2 , in the present disclosure, the pump body assembly further includes a cylinder and a piston 20 , the cylinder is rotatably arranged in the volume cavity of the cylinder liner 40 , a piston hole is opened on the cylinder along its radial direction, and the piston 20 has a sliding hole, and at least a part of the rotating shaft 30 is penetrated in the sliding hole. When the piston 20 rotates with the rotating shaft 30, the piston 20 slides in the piston hole relative to the rotating shaft 30, and the cylinder rotates synchronously.

通过在法兰结构的一侧开设消音凹槽5031，以增加高压气体的流通路径，在消音凹槽5031内开设微孔结构5041进行排气，消音凹槽5031和微孔结构5041配合使用可以有效提高结构的吸声性，降低噪音。法兰结构的端面设置多个微孔结构5041，在转缸压缩机高频率运动的情况下降噪效果不衰减，降噪性能稳定。同时微孔结构5041可提高法兰结构的刚度。通过将法兰结构与消音器一体设计，在转缸压缩机的泵体组件实际运行的过程中，进入消音凹槽内的高压气体在流经消音凹槽规划的消音路径后，能够经法兰排气孔排出，从而完成消音和排气一体化的过程。A muffler groove 5031 is opened on one side of the flange structure to increase the flow path of high-pressure gas, and a microporous structure 5041 is opened in the muffler groove 5031 for exhausting. The combination of the muffler groove 5031 and the microporous structure 5041 can effectively Improve the sound absorption of the structure and reduce the noise. The end face of the flange structure is provided with a plurality of microporous structures 5041, the noise reduction effect is not attenuated and the noise reduction performance is stable under the condition of high frequency motion of the rotary cylinder compressor. At the same time, the microporous structure 5041 can improve the rigidity of the flange structure. By integrating the flange structure with the muffler, during the actual operation of the pump body assembly of the rotary compressor, the high-pressure gas entering the muffler groove can pass through the flange after flowing through the muffler path planned by the muffler groove. The exhaust hole is exhausted to complete the process of integrating muffler and exhaust.

此外，在法兰结构的侧面设置多个微孔结构5041，可以避免高压排气脉冲的直接冲击，有效降低气动噪音。同时微孔结构5041可提高法兰结构的刚度。通过将法兰结构与消音器一体设计，在转缸压缩机的泵体组件实际运行的过程中，进入消音凹槽内的高压气体在流经消音凹槽规划的消音路径后，能够经法兰排气孔排出，从而完成消音和排气一体化的过程。In addition, multiple microporous structures 5041 are arranged on the side of the flange structure, which can avoid the direct impact of the high-pressure exhaust pulse and effectively reduce the aerodynamic noise. At the same time, the microporous structure 5041 can improve the rigidity of the flange structure. By integrating the flange structure with the muffler, during the actual operation of the pump body assembly of the rotary compressor, the high-pressure gas entering the muffler groove can pass through the flange after flowing through the muffler path planned by the muffler groove. The exhaust hole is exhausted to complete the process of integrating muffler and exhaust.

为了改善现有的转缸压缩机在运行过程中，法兰结构安装不稳定产生振动噪音的问题以及法兰结构不具有消音功能的问题，可以通过优化法兰结构使法兰结构具有消音功能，以及在法兰结构上设置连接凸台结构达到实现法兰结构降低振动声噪。In order to improve the problem that the flange structure is unstable to install and generate vibration and noise during the operation of the existing rotary-cylinder compressor, and the flange structure does not have a sound-absorbing function, the flange structure can be optimized to make the flange structure have a sound-absorbing function. And the connection boss structure is arranged on the flange structure to realize the reduction of vibration, noise and noise of the flange structure.

具体地，如图4、图22、图23和图24所示，法兰结构朝向气缸套40的一侧开设有消音凹槽5031，消音凹槽5031沿法兰结构的周向延伸，法兰结构还包括法兰排气孔5011，法兰排气孔5011与消音凹槽5031连通；法兰结构的外周面具有沿法兰结构的径向伸出的连接凸台5051，连接凸台5051为多个，多个连接凸台5051沿法兰结构的周向间隔设置，以在相邻两个连接凸台5051之间形成避空凹部。Specifically, as shown in FIG. 4 , FIG. 22 , FIG. 23 and FIG. 24 , the side of the flange structure facing the cylinder liner 40 is provided with a muffler groove 5031 , and the muffler groove 5031 extends along the circumferential direction of the flange structure. The structure also includes a flange exhaust hole 5011, and the flange exhaust hole 5011 communicates with the muffler groove 5031; the outer peripheral surface of the flange structure has a connection boss 5051 extending along the radial direction of the flange structure, and the connection boss 5051 is A plurality of connecting bosses 5051 are arranged at intervals along the circumferential direction of the flange structure, so as to form a hollow recess between two adjacent connecting bosses 5051 .

由上可知，从以上的描述中，可以看出，本公开上述实施例中，通过在法兰结构的一侧设置周向延伸的消音凹槽5031，以使现法兰结构具有消音功能，且周向延伸的消音凹槽5031增大了气体的流动路径，有效减小了气体流动的噪音。在法兰结构的外周面通过设置多个连接凸台5051以形成避空凹部，达到减振降噪的效果。As can be seen from the above, from the above description, it can be seen that in the above-mentioned embodiments of the present disclosure, a circumferentially extending muffler groove 5031 is provided on one side of the flange structure, so that the existing flange structure has a muffler function, and The circumferentially extending muffler grooves 5031 increase the flow path of the gas and effectively reduce the noise of the gas flow. A plurality of connecting bosses 5051 are arranged on the outer peripheral surface of the flange structure to form a hollow concave portion, so as to achieve the effect of reducing vibration and noise.

具体地，通过在法兰结构的侧面设置周向延伸的消音凹槽5031，气体在进入到消音凹槽5031内部后沿消音凹槽5031的一端向另一端流动，降低气动的噪音，以使法兰结构具有消音功能。法兰结构具有支撑作用，通过在法兰结构的外周面设置多个间隔设置的连接凸台5051，使两个连接凸台5051之间形成避空凹部，在进行安装法兰结构时，通过采用外周面的连接凸台5051进行安装，使安装更加稳定，减少振动声噪，以达到降低噪音的效果。Specifically, by arranging a circumferentially extending muffler groove 5031 on the side of the flange structure, the gas flows along one end of the muffler groove 5031 to the other end after entering the interior of the muffler groove 5031, reducing aerodynamic noise, so that the The blue structure has the function of silencing. The flange structure has a supporting function. By setting a plurality of connecting bosses 5051 arranged at intervals on the outer peripheral surface of the flange structure, a hollow recess is formed between the two connecting bosses 5051. When installing the flange structure, by using The connection boss 5051 on the outer peripheral surface is installed to make the installation more stable and reduce vibration and noise, so as to achieve the effect of reducing noise.

在本公开中，法兰结构上的消音凹槽5031可以连通，也可以不连通，以能使法兰结构通过设置消音凹槽5031达到降低噪音的效果为准。具体地，当消音凹槽5031不连通时，消音凹槽5031的首尾之间形成阻断结构5021，以能使进入到消音凹槽5031内部的气体沿定向路径流动，可以增强降噪效果，同时阻断结构5021可增加法兰结构的刚度，提高法兰结构的稳定性。In the present disclosure, the muffler grooves 5031 on the flange structure may be connected or not, as long as the flange structure can achieve the effect of reducing noise by providing the muffler grooves 5031 . Specifically, when the muffler groove 5031 is not in communication, a blocking structure 5021 is formed between the head and tail of the muffler groove 5031, so that the gas entering the muffler groove 5031 can flow along a directional path, which can enhance the noise reduction effect, and at the same time The blocking structure 5021 can increase the rigidity of the flange structure and improve the stability of the flange structure.

如图22所示，相邻两个连接凸台5051之间的距离相等。通过多个沿法兰结构周向等距离间隔设置的连接凸台5051进行安装时，法兰结构受力均匀，减少集中应力，可使法兰结构安装稳定减小振动噪音。As shown in FIG. 22 , the distance between two adjacent connecting bosses 5051 is the same. When installing through a plurality of connecting bosses 5051 arranged at equal intervals along the circumferential direction of the flange structure, the flange structure is uniformly stressed, reducing concentrated stress, which can stabilize the installation of the flange structure and reduce vibration and noise.

需要说明的是，相邻的两个连接凸台5051间的距离也可以不相等，由于多个连接凸台5051的形状可以是至少一部分相同，也可以是全不相同，由于组合形式较多，此处不一一列举。两个连接凸台5051间的距离具体以相邻两个连接凸台5051的形状的不同可能存在微差，具体以能减小法兰结构安装时的集中应力，加强安装的稳定性为准。It should be noted that the distance between two adjacent connecting bosses 5051 may also be unequal, because the shapes of the plurality of connecting bosses 5051 may be at least partially the same, or may be completely different. Not listed here. The distance between the two connecting bosses 5051 may be slightly different depending on the shape of the two adjacent connecting bosses 5051 , which can reduce the concentrated stress during installation of the flange structure and enhance the stability of the installation.

如图23所示，在法兰结构的轴向上，连接凸台5051延伸至法兰结构的外周面的两端。连接凸台5051延伸至法兰结构的外周面的两端以增大连接凸台5051与法兰结构的接触面积，减小集中应力，提高转缸压缩机运行的过程中法兰结构安装的稳定性避免出现振动噪音。As shown in FIG. 23 , in the axial direction of the flange structure, the connecting bosses 5051 extend to both ends of the outer peripheral surface of the flange structure. The connecting bosses 5051 extend to both ends of the outer peripheral surface of the flange structure to increase the contact area between the connecting bosses 5051 and the flange structure, reduce the concentrated stress, and improve the installation stability of the flange structure during the operation of the rotary compressor. to avoid vibration noise.

具体地，各连接凸台5051上均设置有至少一个焊点5061，各个连接凸台5051上至少一个焊点5061，以增强焊接的稳定性，焊接点越多对应的连接凸台5051的稳定性越高。Specifically, each connection boss 5051 is provided with at least one solder joint 5061, and each connection boss 5051 has at least one solder joint 5061 to enhance the stability of welding. higher.

需要说明的是，连接凸台5051上不限于通过焊点5061的方式进行焊接，也可以通过焊条的方式进行焊接，以能达到法兰结构稳定并减小振动噪音的效果为准。It should be noted that, the connection boss 5051 is not limited to welding through the welding point 5061, but can also be welded through the welding rod, which can achieve the effect of stabilizing the flange structure and reducing vibration and noise.

根据连接凸台5051的个数不同，本申请提供了图22的实施例，其中有六个连接凸台5051。此外，还提供了图24的实施例，其中有三个连接凸台5051。当然，连接凸台5051的个数还可以是两个、四个、五个等，由于可替代的方式较多，这里就不一一列举了。According to the number of the connection bosses 5051 , the present application provides the embodiment of FIG. 22 , in which there are six connection bosses 5051 . In addition, the embodiment of FIG. 24 is provided in which there are three connection bosses 5051. Of course, the number of the connecting bosses 5051 may also be two, four, five, etc., and since there are many alternative ways, they will not be listed here.

通过在法兰结构的一侧设置周向延伸的消音凹槽5031，以使现法兰结构具有消音功能，且周向延伸的消音凹槽5031增大了气体的流动路径，有效减小了气体流动的噪音。在法兰结构的外周面通过设置多个连接凸台5051以形成避空凹部，达到减振降噪的效果。目前现有的转缸压缩机需要与消音器配合使用以进行降噪消音，且法兰结构的安装强度较低，易产生振动噪音。By arranging a circumferentially extending sound-absorbing groove 5031 on one side of the flange structure, the existing flange structure has a sound-absorbing function, and the circumferentially extending sound-absorbing groove 5031 increases the flow path of the gas and effectively reduces the gas flow rate. Flow noise. A plurality of connecting bosses 5051 are arranged on the outer peripheral surface of the flange structure to form a hollow concave portion, so as to achieve the effect of reducing vibration and noise. At present, the existing rotary cylinder compressor needs to be used in conjunction with a muffler for noise reduction and noise reduction, and the installation strength of the flange structure is low, which is prone to vibration and noise.

具体地，通过在法兰结构的侧面设置周向延伸的消音凹槽5031，气体在进入到消音凹槽5031内部后沿消音凹槽5031的一端向另一端流动，降低气动的噪音，以使法兰结构具有消音功能。法兰结构具有支撑作用，通过在法兰结构的外周面设置多个间隔设置的连接凸台5051，使两个连接凸台5051间形成避空凹部，在进行安装法兰结构时，通过采用外周面的连接凸台5051进行安装，使安装更加稳定，减少振动声噪。以达到降低噪音的效果。Specifically, by arranging a circumferentially extending muffler groove 5031 on the side of the flange structure, the gas flows along one end of the muffler groove 5031 to the other end after entering the interior of the muffler groove 5031, reducing aerodynamic noise, so that the The blue structure has the function of silencing. The flange structure has a supporting function. By arranging a plurality of connecting bosses 5051 at intervals on the outer peripheral surface of the flange structure, a hollow recess is formed between the two connecting bosses 5051. When installing the flange structure, the outer circumference is used. The connection boss 5051 on the surface is installed to make the installation more stable and reduce vibration and noise. to reduce noise.

为了改善现有的转缸压缩机在运行过程中，法兰结构安装不稳定产生振动噪音的问题以及法兰结构不具有消音功能的问题，可以通过优化法兰结构使法兰结构具有消音功能，以及在法兰结构上设置连接凸台结构并通过焊点焊接的方式达到降低法兰结构振动声噪。In order to improve the problem that the flange structure is unstable to install and generate vibration and noise during the operation of the existing rotary-cylinder compressor, and the flange structure does not have a sound-absorbing function, the flange structure can be optimized to make the flange structure have a sound-absorbing function. And a connection boss structure is arranged on the flange structure, and the vibration and noise of the flange structure is reduced by means of spot welding.

具体地，如图25至图34所示，法兰结构的外周面具有沿法兰结构的径向伸出的连接凸台5051，连接凸台5051为多个，多个连接凸台5051沿法兰结构的周向间隔设置，以在相邻两个连接凸台5051之间形成避空凹部，连接凸台5051上设有焊点5061，焊点5061的直径大于等于4mm且小于等于7mm。Specifically, as shown in FIGS. 25 to 34 , the outer peripheral surface of the flange structure has connection bosses 5051 extending along the radial direction of the flange structure, there are multiple connection bosses 5051, and the plurality of connection bosses 5051 are along the The blue structures are arranged at intervals in the circumferential direction to form a hollow recess between two adjacent connection bosses 5051. The connection bosses 5051 are provided with solder joints 5061, and the diameter of the solder joints 5061 is greater than or equal to 4mm and less than or equal to 7mm.

由上可知，从以上的描述中，可以看出，本公开上述实施例中，法兰结构的周向间隔设置连接凸台5051，通过连接凸台5051安装法兰结构，可提高法兰结构的刚度，减小热变形，以提高法兰结构的稳定性减小振动噪音。As can be seen from the above, from the above description, it can be seen that in the above-mentioned embodiments of the present disclosure, connecting bosses 5051 are arranged at intervals in the circumferential direction of the flange structure. Rigidity, reduce thermal deformation, improve the stability of flange structure and reduce vibration noise.

具体地，通过在法兰结构的轴向设置间隔设置的连接凸台5051，通过焊接连接凸台5051，实现固定法兰结构的效果，可加强焊接刚度，在转缸压缩机运行的过程中，在连接凸台5051上进行点焊，且点焊的大小在4mm到7mm以优化焊接方式，可降低转缸压缩机运行过程中法兰结构受到的振动激励，有效提高了法兰结构的稳定性，并降低了振动噪音。Specifically, by arranging the connecting bosses 5051 at intervals in the axial direction of the flange structure, and by welding the connecting bosses 5051, the effect of fixing the flange structure can be achieved, and the welding rigidity can be strengthened. Spot welding is carried out on the connecting boss 5051, and the size of the spot welding is 4mm to 7mm to optimize the welding method, which can reduce the vibration excitation of the flange structure during the operation of the rotary compressor, and effectively improve the stability of the flange structure. , and reduce vibration noise.

如图25至图34所示，相邻两个连接凸台5051之间的距离相等。通过多个沿法兰结构周向等距离间隔设置的连接凸台5051进行安装时，法兰结构受力均匀，减少集中应力，可使法兰结构安装稳定减小振动噪音。As shown in FIG. 25 to FIG. 34 , the distance between two adjacent connecting bosses 5051 is the same. When installing through a plurality of connecting bosses 5051 arranged at equal intervals along the circumferential direction of the flange structure, the flange structure is uniformly stressed, reducing concentrated stress, which can stabilize the installation of the flange structure and reduce vibration and noise.

如图26、图28、图30、图32和图34所示，在法兰结构的轴向上，连接凸台5051延伸至法兰结构的外周面的两端。连接凸台5051延伸至法兰结构的外周面的两端以增大连接凸台5051与法兰结构的接触面积，减小集中应力，提高转缸压缩机运行的过程中法兰结构安装的稳定性避免出现振动噪音。As shown in FIGS. 26 , 28 , 30 , 32 and 34 , in the axial direction of the flange structure, the connection bosses 5051 extend to both ends of the outer peripheral surface of the flange structure. The connecting bosses 5051 extend to both ends of the outer peripheral surface of the flange structure to increase the contact area between the connecting bosses 5051 and the flange structure, reduce the concentrated stress, and improve the installation stability of the flange structure during the operation of the rotary compressor. to avoid vibration noise.

根据连接凸台5051的个数不同，本申请提供了图27、28、31、32的实施例，其中有六个连接凸台5051。此外，还提供了图25、26、29、30的实施例，其中有三个连接凸台5051。另外，还提供了图33、34的实施例，其中有四个连接凸台5051。当然，连接凸台5051的个数还可以是两个、五个等，由于可替代的方式较多，这里就不一一列举了。According to the number of the connection bosses 5051, the present application provides the embodiments of FIGS. 27 , 28 , 31 and 32 , in which there are six connection bosses 5051 . In addition, the embodiments of Figures 25, 26, 29, 30 are also provided, wherein there are three connection bosses 5051. In addition, the embodiment of Figures 33 and 34 is also provided in which there are four connection bosses 5051. Of course, the number of the connection bosses 5051 may also be two, five, etc. Since there are many alternative ways, they will not be listed here.

如图25至图34所示，各连接凸台5051上均设置有至少一个焊点5061。每个连接凸台5051上均设置至少一个焊点5061。具体地，焊点5061可以是一个、两个或者多个。根据法兰结构在泵体组件中的实际受力情况，各个连接凸台5051上的焊点5061的数量可以至少一部分相同，也可以均不相同，以能达到减振降噪的效果为准，当各个连接凸台5051上的焊点5061的数量至少一部分相同时，由于组合形式过多，因此对不同的实施方式不一一进行列举。下面以各连接凸台5051上的焊点5061数量均相同的实施方式进行说明。As shown in FIG. 25 to FIG. 34 , each of the connection bosses 5051 is provided with at least one solder joint 5061 . At least one solder joint 5061 is provided on each connection boss 5051 . Specifically, the number of solder joints 5061 may be one, two or more. According to the actual force of the flange structure in the pump body assembly, the number of solder joints 5061 on each connection boss 5051 may be at least partially the same, or may be different, subject to the effect of reducing vibration and noise. When at least a part of the number of solder joints 5061 on each connection boss 5051 is the same, since there are too many combinations, different embodiments are not listed one by one. The following description will be given by taking the embodiment in which the number of solder joints 5061 on each connection boss 5051 is the same.

需要说明的是，当同一个连接凸台5051上设置有多个焊点5061时，多个焊点5061沿法兰结构的轴向间隔设置。It should be noted that when a plurality of welding points 5061 are provided on the same connection boss 5051, the multiple welding points 5061 are arranged at intervals along the axial direction of the flange structure.

如图30和图34所示的具体实施方式中，当同一个连接凸台5051上设置有两个焊点5061时，所有连接凸台5051上的位于上侧的焊点5061均位于法兰结构的轴向的同一高度上，所有连接凸台5051上的位于下侧的焊点5061均位于法兰结构的轴向的同一高度上。In the specific implementation shown in FIGS. 30 and 34 , when two solder joints 5061 are provided on the same connection boss 5051, all the solder joints 5061 on the upper side of the connection boss 5051 are located in the flange structure At the same height in the axial direction of the flange structure, all the welding points 5061 on the lower side of the connection bosses 5051 are located at the same height in the axial direction of the flange structure.

具体地，连接凸台5051在法兰结构的周向间隔设置，且连接凸台5051上的焊点5061设置为同一高度，可改善多个方向的振动传递，以增强焊接的刚度，降低振动噪音。Specifically, the connecting bosses 5051 are arranged at intervals in the circumferential direction of the flange structure, and the welding points 5061 on the connecting bosses 5051 are set to the same height, which can improve the vibration transmission in multiple directions, enhance the rigidity of welding, and reduce vibration noise. .

如图26和图28所示的具体实施方式中，各连接凸台5051上均设置有一个焊点5061，所有连接凸台5051上的焊点5061均位于法兰结构的轴向的同一高度上。可改善多个方向的振动传递，以增强焊接的刚度，降低振动噪音。In the specific embodiment shown in FIG. 26 and FIG. 28 , each connecting boss 5051 is provided with a welding spot 5061, and the welding spots 5061 on all connecting bosses 5051 are located at the same height in the axial direction of the flange structure . Vibration transmission in multiple directions can be improved to enhance welding stiffness and reduce vibration noise.

如图32所示的具体实施方式中，各连接凸台5051上均设置有一个焊点5061，所有连接凸台5051上的焊点5061交替位于法兰结构的轴向的第一位置和第二位置处，第一位置位于第二位置的上方，且不同连接凸台5051的第一位置位于法兰结构的轴向的同一高度上，不同连接凸台5051的第二位置位于法兰结构的轴向的同一高度上。焊点5061在多个连接凸台5051上交替设置，可缓冲法兰结构收到的多个方向的振动，提高焊接的刚度，以降低振动噪音。In the specific embodiment shown in FIG. 32 , each connecting boss 5051 is provided with a welding spot 5061, and the welding spots 5061 on all connecting bosses 5051 are alternately located at the first and second axial positions of the flange structure. At the position, the first position is located above the second position, and the first positions of the different connecting bosses 5051 are located at the same height in the axial direction of the flange structure, and the second positions of the different connecting bosses 5051 are located at the axis of the flange structure. to the same height. The welding points 5061 are alternately arranged on a plurality of connecting bosses 5051, which can buffer the vibrations received by the flange structure in multiple directions, improve the rigidity of welding, and reduce vibration and noise.

如图25至图34所示，相邻两个连接凸台5051分别至法兰结构的轴线的两条连线之间夹角为60度或90度或120度。As shown in FIG. 25 to FIG. 34 , the included angle between two connecting lines from two adjacent connecting bosses 5051 to the axis of the flange structure is 60 degrees or 90 degrees or 120 degrees.

具体地，当通过三个焊点5061进行焊接时，连接凸台5051设置三个，相邻两个连接凸台5051分别至法兰结构的轴线的两条连线之间夹角为120度，且每个连接凸台5051上均设置一个焊点5061；当通过六个焊点5061进行焊接时，连接凸台5051设置六个，相邻两个连接凸台5051分别至法兰结构的轴线的两条连线之间夹角为60度，且每个连接凸台5051上均设置一个焊点5061；当通过六个焊点5061进行焊接时，连接凸台5051设置三个，邻两个连接凸台5051分别至法兰结构的轴线的两条连线之间夹角为120度，且每个连接凸台5051上均设置两个焊点5061；当通过八个焊点5061进行焊接时，连接凸台5051设置四个，相邻两个连接凸台5051分别至法兰结构的轴线的两条连线之间夹角为90度，且每个连接凸台5051上均设置两个焊点5061。Specifically, when welding is performed through three welding points 5061, three connecting bosses 5051 are provided, and the included angle between two connecting lines from two adjacent connecting bosses 5051 to the axis of the flange structure is 120 degrees, And each connection boss 5051 is provided with one welding spot 5061; when welding is performed through six welding spots 5061, six connecting bosses 5051 are provided, and two adjacent connecting bosses 5051 are respectively connected to the axis of the flange structure. The included angle between the two connecting lines is 60 degrees, and each connection boss 5051 is provided with one solder joint 5061; when welding is performed through six solder joints 5061, three connection bosses 5051 are arranged, and two adjacent ones are connected. The included angle between the two connecting lines from the bosses 5051 to the axis of the flange structure is 120 degrees, and each connecting boss 5051 is provided with two welding points 5061; when welding is performed through eight welding points 5061, Four connecting bosses 5051 are provided, and the included angle between the two connecting lines from two adjacent connecting bosses 5051 to the axis of the flange structure is 90 degrees, and each connecting boss 5051 is provided with two welding points 5061.

需要说明的是，根据焊点5061个数的不同，可对连接凸台5051的个数及角度设置进行适应性调整，以加强焊接强度，降低振动噪音。It should be noted that, according to the difference in the number of solder joints 5061, the number and angle setting of the connection bosses 5051 can be adjusted adaptively, so as to strengthen the soldering strength and reduce vibration and noise.

如图25至图34所示，法兰结构朝向气缸套40的一侧开设有消音凹槽5031。法兰结构具有法兰排气孔5011，通过在法兰结构的侧面设置周向延伸的消音凹槽5031，气体在进入到消音凹槽5031内部后沿消音凹槽5031的一端向另一端流动至法兰排气孔5011，降低气动的噪音，以使法兰结构具有消音功能。As shown in FIG. 25 to FIG. 34 , the side of the flange structure facing the cylinder liner 40 is provided with a muffler groove 5031 . The flange structure has a flange exhaust hole 5011. By setting a circumferentially extending muffler groove 5031 on the side of the flange structure, the gas flows along one end of the muffler groove 5031 to the other end after entering the interior of the muffler groove 5031. Flange exhaust hole 5011, reduce the aerodynamic noise, so that the flange structure has the function of silencing.

如图25至图34所示，消音凹槽5031的侧壁具有向法兰结构的中心轴突出的筋状结构，筋状结构为多个，多个筋状结构沿消音凹槽5031的侧壁间隔设置，以使消音凹槽5031具有交替设置的宽过流区域和窄过流区域。As shown in FIG. 25 to FIG. 34 , the side wall of the muffler groove 5031 has a rib-like structure protruding toward the central axis of the flange structure, and there are multiple rib-shaped structures along the side wall of the muffler groove 5031 They are spaced so that the muffler grooves 5031 have alternately arranged wide and narrow flow regions.

通过在法兰结构的周向间隔设置连接凸台5051，通过连接凸台5051安装法兰结构，可提高法兰结构的刚度，减小热变形，以提高法兰结构的稳定性减小振动噪音。目前现有的法兰结构采用悬臂支撑的方式进行安装，易产生振动噪音，导致降噪效果不稳定，不利于进行降低噪音。By arranging connecting bosses 5051 at intervals in the circumferential direction of the flange structure, and installing the flange structure through the connecting bosses 5051, the rigidity of the flange structure can be improved, the thermal deformation can be reduced, the stability of the flange structure can be improved, and the vibration noise can be reduced. . At present, the existing flange structure is installed by cantilever support, which is prone to vibration and noise, resulting in unstable noise reduction effect, which is not conducive to noise reduction.

具体地，通过在法兰结构的轴向设置间隔设置的连接凸台5051结构，通过焊接连接凸台5051，实现固定法兰结构的效果，可加强焊接刚度，在转缸压缩机运行的过程中，在连接凸台5051上进行点焊，且点焊的大小在4mm到7mm以优化焊接方式，可降低转缸压缩机运行过程中法兰结构受到的振动激励，有效提高了法兰结构的稳定性，并降低了振动噪音。Specifically, by arranging the connecting bosses 5051 at intervals in the axial direction of the flange structure, and by welding the connecting bosses 5051, the effect of fixing the flange structure can be achieved, and the welding rigidity can be strengthened. During the operation of the rotary cylinder compressor , Spot welding is performed on the connecting boss 5051, and the size of the spot welding is 4mm to 7mm to optimize the welding method, which can reduce the vibration excitation of the flange structure during the operation of the rotary compressor, and effectively improve the stability of the flange structure. and reduce vibration noise.

显然，上述所描述的实施例仅仅是本公开一部分的实施例，而不是全部的实施例。基于本公开中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都应当属于本公开保护的范围。Obviously, the above-described embodiments are only a part of the embodiments of the present disclosure, but not all of the embodiments. Based on the embodiments in the present disclosure, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present disclosure.

需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、工作、器件、组件和/或它们的组合。It should be noted that the terminology used herein is for the purpose of describing specific embodiments only, and is not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly dictates otherwise, the singular is intended to include the plural as well, furthermore, it is to be understood that when the terms "comprising" and/or "including" are used in this specification, it indicates that There are features, steps, acts, devices, components, and/or combinations thereof.

需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式能够以除了在这里图示或描述的那些以外的顺序实施。It should be noted that the terms "first", "second", etc. in the description and claims of the present application and the above drawings are used to distinguish similar objects, and are not necessarily used to describe a specific sequence or sequence. It is to be understood that data so used may be interchanged under appropriate circumstances so that the embodiments of the application described herein can be practiced in sequences other than those illustrated or described herein.

以上所述仅为本公开的优选实施例而已，并不用于限制本公开，对于本领域的技术人员来说，本公开可以有各种更改和变化。凡在本公开的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本公开的保护范围之内。The above descriptions are only preferred embodiments of the present disclosure, and are not intended to limit the present disclosure. For those skilled in the art, the present disclosure may have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present disclosure shall be included within the protection scope of the present disclosure.

Claims

一种法兰结构，其中所述法兰结构朝向气缸套(40)的一侧开设有消音通道，所述消音通道沿所述法兰结构的周向延伸，所述法兰结构还包括法兰排气孔(5011)，所述法兰排气孔(5011)与所述消音通道连通。A flange structure, wherein the side of the flange structure facing the cylinder liner (40) is provided with a muffler channel, the muffler channel extends along the circumferential direction of the flange structure, and the flange structure further comprises a flange An exhaust hole (5011), the flange exhaust hole (5011) communicates with the muffler passage.
根据权利要求1所述的法兰结构，其中所述消音通道首尾连通，或所述消音通道的首尾不连通。The flange structure according to claim 1, wherein the muffler passages are connected end to end, or the muffler passages are not communicated end to end.
根据权利要求1或2所述的法兰结构，其中所述消音通道由一个连续的消音凹槽(5031)构成。The flange structure according to claim 1 or 2, wherein the muffler channel is formed by a continuous muffler groove (5031).
根据权利要求3所述的法兰结构，其中所述消音凹槽(5031)的侧壁具有向所述法兰结构的中心轴突出的筋状结构，所述筋状结构为多个，多个所述筋状结构沿所述消音凹槽(5031)的侧壁间隔设置，以使所述消音通道具有交替设置的宽过流区域和窄过流区域。The flange structure according to claim 3, wherein the side wall of the muffler groove (5031) has a rib-like structure protruding toward the central axis of the flange structure, and the rib-like structure is a plurality of The rib-like structures are arranged at intervals along the sidewall of the muffler groove (5031), so that the muffler channel has alternately arranged wide flow regions and narrow flow regions.
根据权利要求4所述的法兰结构，其中The flange structure of claim 4, wherein

不同的所述筋状结构与所述法兰结构的中心轴之间的距离相等；或者The distances between the different rib-like structures and the central axis of the flange structures are equal; or

至少两个所述筋状结构与所述法兰结构的中心轴之间的距离不相等。The distances between at least two of the tendon structures and the central axis of the flange structure are not equal.
根据权利要求4或5所述的法兰结构，其中所述筋状结构的个数大于3个且小于5个。The flange structure according to claim 4 or 5, wherein the number of the rib-like structures is greater than 3 and less than 5.
根据权利要求1-6中任一所述的法兰结构，其中所述法兰结构具有多个消音凹槽(5031)，多个所述消音凹槽(5031)沿所述法兰结构的周向间隔设置，且相邻两个所述消音凹槽(5031)通过连通孔连通。The flange structure according to any one of claims 1-6, wherein the flange structure has a plurality of sound-absorbing grooves (5031), and the plurality of the sound-absorbing grooves (5031) are along the circumference of the flange structure They are arranged at intervals, and two adjacent muffler grooves (5031) communicate with each other through communication holes.
根据权利要求1-7任一所述的法兰结构，其中所述法兰结构具有法兰孔，所述法兰孔与所述法兰结构的中心轴偏心设置。The flange structure according to any one of claims 1-7, wherein the flange structure has a flange hole, and the flange hole is eccentrically arranged with the central axis of the flange structure.
根据权利要求8所述的法兰结构，其中所述法兰结构的中部具有轴颈(5071)，所述轴颈(5071)由开设所述消音通道后的部分构成，所述法兰孔贯穿所述轴颈(5071)的轴向端面。The flange structure according to claim 8, wherein a journal (5071) is provided in the middle of the flange structure, the journal (5071) is formed by the part after the muffler channel is opened, and the flange hole penetrates through The axial end face of the journal (5071).
根据权利要求9所述的法兰结构，其中所述轴颈(5071)的外周圆与所述法兰结构的外周圆同轴。The flange structure according to claim 9, wherein the outer circumference of the journal (5071) is coaxial with the outer circumference of the flange structure.
根据权利要求9或10所述的法兰结构，其中所述轴颈(5071)背离气缸套(40)的一侧具有突出于所述法兰结构的端面的凸环结构，以使所述法兰结构的轴向上的总高度H大于所述法兰结构的轴向上的两端面之间的高度H1，所述消音通道在所述法兰结构的轴向上的高度H2小于所述法兰结构的轴向上的两端面之间的高度H1。The flange structure according to claim 9 or 10, wherein the side of the journal (5071) facing away from the cylinder liner (40) has a convex ring structure protruding from the end face of the flange structure, so that the method The total height H of the flange structure in the axial direction is greater than the height H1 between the two end faces of the flange structure in the axial direction, and the height H2 of the muffler passage in the axial direction of the flange structure is smaller than the height H2 of the flange structure. The height H1 between the two end faces in the axial direction of the blue structure.
根据权利要求11所述的法兰结构，其中The flange structure of claim 11, wherein

0.5H<H1<0.9H；和/或0.5H<H1<0.9H; and/or

0.3H<H2<0.7H。0.3H<H2<0.7H.
根据权利要求12所述的法兰结构，其中The flange structure of claim 12, wherein

0.65H<H1<0.75H；和/或0.65H<H1<0.75H; and/or

0.4H<H2<0.6H。0.4H<H2<0.6H.
根据权利要求11所述的法兰结构，其中所述法兰结构的侧壁厚度L1、所述法兰结构的端面厚度L2满足如下的关系：The flange structure according to claim 11, wherein the side wall thickness L1 of the flange structure and the end face thickness L2 of the flange structure satisfy the following relationship:

0.05H<L1<0.25H；0.05H<L1<0.25H;

0.1H<L2<0.4H。0.1H<L2<0.4H.
根据权利要求11的法兰结构，其中消音通道的侧壁具有向法兰结构的中心轴突出的筋状结构，轴颈(5071)的轴向端面的最小厚度L3与筋状结构至轴颈(5071)的中心k2之间的距离R3之间的关系为0.05H<L3<R3。The flange structure according to claim 11, wherein the side wall of the muffler channel has a rib-like structure protruding toward the central axis of the flange structure, and the minimum thickness L3 of the axial end face of the journal (5071) is the same as the rib-like structure to the journal (5071). 5071), the relationship between the distances R3 between the centers k2 is 0.05H<L3<R3.
根据权利要求4的法兰结构，其中法兰结构的中部具有轴颈(5071)，轴颈(5071)的中心k2与法兰结构的法兰轴孔中心k1之间具有偏心量e，法兰结构的法兰轴孔中心k1与消音凹槽(5031)的外侧槽壁之间的距离为R1，筋状结构至轴颈(5071)的中心k2的距离为R3，由轴颈(5071)的中心k2至消音凹槽(5031)的内侧槽壁之间的距离为R2，且R1、R2、R3之间满足如下关系：The flange structure according to claim 4, wherein the middle of the flange structure has a journal (5071), and there is an eccentricity e between the center k2 of the journal (5071) and the center k1 of the flange shaft hole of the flange structure, and the flange The distance between the center k1 of the flange shaft hole of the structure and the outer groove wall of the muffler groove (5031) is R1, and the distance from the rib-shaped structure to the center k2 of the journal (5071) is R3. The distance between the center k2 and the inner groove wall of the muffler groove (5031) is R2, and the following relationship is satisfied between R1, R2, and R3:

0.1<(R1-R2)/(R3-R2)<0.4。0.1<(R1-R2)/(R3-R2)<0.4.
根据权利要求16所述的法兰结构，其中0.15<(R1-R2)/(R3-R2)<0.25。The flange structure according to claim 16, wherein 0.15<(R1-R2)/(R3-R2)<0.25.
根据权利要求16或17所述的法兰结构，其中The flange structure according to claim 16 or 17, wherein

各所述宽过流区域处的距离R1均相等，以构成参考第一参考圆；The distances R1 at each of the wide overcurrent regions are equal to form a reference first reference circle;

各所述窄过流区域处的距离R3均相等，以构成参考第二参考圆；The distances R3 at each of the narrow overcurrent regions are equal to form a reference second reference circle;

各所述宽过流区域和所述窄过流区域处的距离R2均相等，以构成参考第三参考圆。The distances R2 at each of the wide flow area and the narrow flow area are equal to form a reference third reference circle.
根据权利要求1-18中任一所述的法兰结构，其中所述法兰结构为上法兰(50)。The flange structure according to any one of claims 1-18, wherein the flange structure is an upper flange (50).
一种泵体组件，其中包括权利要求1至19中任一项所述的法兰结构。A pump body assembly comprising the flange structure of any one of claims 1 to 19.
根据权利要求20所述的泵体组件，其中所述泵体组件还包括：The pump body assembly of claim 20, wherein the pump body assembly further comprises:

转轴(30)；shaft (30);

限位板，所述限位板具有限位板排气孔(7011)；a limit plate, the limit plate has a limit plate exhaust hole (7011);

气缸套(40)，所述气缸套(40)具有气缸套排气孔(4012)，所述转轴(30)依次穿过所述法兰结构、所述限位板和所述气缸套(40)，所述气缸套排气孔(4012)、所述限位板排气孔(7011)和所述法兰结构的消音通道连通。A cylinder liner (40), the cylinder liner (40) has a cylinder liner exhaust hole (4012), and the rotating shaft (30) passes through the flange structure, the limiting plate and the cylinder liner (40) in sequence ), the cylinder liner exhaust hole (4012), the limit plate exhaust hole (7011) and the muffler channel of the flange structure communicate with each other.
根据权利要求21所述的泵体组件，其中所述气缸套(40)具有容积腔所述泵体组件还包括：The pump body assembly according to claim 21, wherein the cylinder liner (40) has a volume cavity and the pump body assembly further comprises:

气缸(10)，所述气缸(10)可转动地设置在所述容积腔内，所述气缸(10)上沿其径向开设有活塞孔；A cylinder (10), the cylinder (10) is rotatably arranged in the volume cavity, and a piston hole is opened on the cylinder (10) along its radial direction;

活塞(20)，所述活塞(20)具有滑移孔，所述转轴(30)的至少一部分穿设在所述滑移孔内，所述活塞(20)随所述转轴(30)转动的过程中，所述活塞(20)相对于所述转轴(30)在所述活塞孔内滑动，且所述气缸(10)同步转动。A piston (20), the piston (20) has a sliding hole, at least a part of the rotating shaft (30) is penetrated in the sliding hole, and the piston (20) rotates with the rotating shaft (30) During the process, the piston (20) slides in the piston hole relative to the rotating shaft (30), and the cylinder (10) rotates synchronously.
根据权利要求21或22所述的泵体组件，其中所述限位板排气孔(7011)为多个，多个所述限位板排气孔(7011)间隔设置。The pump body assembly according to claim 21 or 22, wherein the limit plate exhaust holes (7011) are multiple, and the multiple limit plate exhaust holes (7011) are arranged at intervals.
根据权利要求21-23中任一所述的泵体组件，其中至少两个所述限位板排气孔(7011)的大小不同。The pump body assembly according to any one of claims 21-23, wherein at least two of the limiting plate vent holes (7011) have different sizes.
根据权利要求21-23中任一所述的泵体组件，其中所述气缸套排气孔(4012)为多个，所述气缸套(40)具有多个中间腔(4013)，各所述中间腔(4013)均通过对应的所述气缸套排气孔(4012)与所述气缸套(40)的容积腔连通，所述气缸套(40)还具有与各所述中间腔(4013)连通的多个气缸套连通孔(4011)，多个所述气缸套连通孔(4011)与多个所述限位板排气孔(7011)一一对应设置。The pump body assembly according to any one of claims 21-23, wherein the cylinder liner exhaust hole (4012) is plural, and the cylinder liner (40) has a plurality of intermediate cavities (4013), each of the The intermediate chambers (4013) are all communicated with the volume chambers of the cylinder liner (40) through the corresponding cylinder liner exhaust holes (4012), and the cylinder liner (40) also has a connection with each of the intermediate chambers (4013) A plurality of cylinder liner communication holes (4011) are communicated, and the plurality of cylinder liner communication holes (4011) are provided in a one-to-one correspondence with a plurality of the limit plate exhaust holes (7011).
根据权利要求25所述的泵体组件，其中The pump body assembly of claim 25, wherein

多个所述气缸套排气孔(4012)中的至少两个所述气缸套排气孔(4012)的大小不同；和/或At least two of the cylinder liner exhaust holes (4012) in the plurality of cylinder liner exhaust holes (4012) have different sizes; and/or

各所述中间腔(4013)彼此不连通；和/或each of the intermediate cavities (4013) are not in communication with each other; and/or

多个所述气缸套连通孔(4011)的至少两个所述气缸套连通孔(4011)的大小不同。At least two of the cylinder liner communication holes (4011) of the plurality of cylinder liner communication holes (4011) have different sizes.
根据权利要求21-23中任一所述的泵体组件，其中所述限位板排气孔(7011)与所述法兰结构的法兰排气孔(5011)在所述法兰结构的周向上间隔设置。The pump body assembly according to any one of claims 21-23, wherein the limit plate exhaust hole (7011) and the flange exhaust hole (5011) of the flange structure are in the flange structure. Circumferentially spaced settings.
根据权利要求27所述的泵体组件，其中所述限位板排气孔(7011)与所述法兰排气孔(5011)在所述法兰结构的周向上间隔角度160度至200度。The pump body assembly according to claim 27, wherein the limit plate exhaust hole (7011) and the flange exhaust hole (5011) are spaced at an angle of 160 degrees to 200 degrees in the circumferential direction of the flange structure .
一种流体机械，其中包括权利要求20至28中任一项所述的泵体组件。A fluid machine comprising the pump body assembly of any one of claims 20 to 28.