Annular distributor, compressor and air conditioner thereof

Abstract

The application provides a ring-shaped distributor, a compressor and an air conditioner thereof. The ring-shaped distributor is sleeved on an outer shell of the compressor. The outer shell is provided with a suction port. The ring-shaped distributor is provided with an exhaust port. The suction port is located outside the ring-shaped distributor. The ring-shaped distributor further comprises a suction pipe. An inlet end of the suction pipe is communicated with the ring-shaped distributor through the exhaust port. An outlet end of the suction pipe is communicated with the suction port. The suction pipe comprises a second section pipe. The second section pipe extends along a tangential direction of the outer shell. Thus, the technical problem that when the compressor is provided with the ring-shaped distributor, pressure pulsation generates great vibration when entering the suction pipe is solved.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of compressor, in particular to a ring-shaped distributor, a compressor and an air conditioner thereof. BACKGROUND

[0002] The ring-shaped distributor is set around the compressor, which not only reduces the size of the compressor used in air conditioner, but also improves the noise of the compressor. The ring-shaped distributor becomes an important structure of the distributor of the compressor. Since the distributor is more compact with the shell of the compressor, the pressure pulsation generated by the pump body produces greater vibration when entering the pipeline between the outlet of the communication distributor and the suction port of the pump body, which leads to unstable operation of the compressor.

[0003] For the compressor provided with the ring-shaped distributor, how to reduce the vibration generated when the pressure pulsation enters the suction pipe is a technical problem to be solved at present. SUMMARY

[0004] Therefore, the present application provides a ring-shaped distributor, a compressor and an air conditioner thereof, which can solve the technical problem of the suction pipe of the compressor generating greater resistance to gas when the compressor is provided with the ring-shaped distributor in the prior art.

[0005] In one aspect, the present application provides a ring-shaped distributor, which is sleeved on the shell of a compressor, the shell is provided with a suction port, and the ring-shaped distributor is provided with an exhaust port. The suction port is located outside the ring-shaped distributor, and the ring-shaped distributor further comprises a suction pipe, an inlet end of the suction pipe is communicated with the ring-shaped distributor through the exhaust port, and an outlet end of the suction pipe is communicated with the suction port.

[0006] The suction pipe comprises a second section pipe, and the second section pipe extends along the tangential direction of the shell.

[0007] In some embodiments, the suction pipe further comprises a first section pipe, a third section pipe, a first elbow pipe and a second elbow pipe. The first section pipe is communicated with the ring-shaped distributor through the exhaust port, and the third section pipe is communicated with the suction port. The first section pipe and the second section pipe are communicated through the first elbow pipe, and the second section pipe and the third section pipe are communicated through the second elbow pipe.

[0008] In some embodiments, in the projection of the axial direction of the ring-shaped distributor, the line connecting the center of the suction port and the center of the ring-shaped distributor is L1, the line connecting the center of the exhaust port and the center of the ring-shaped distributor is L2, the included angle between L1 and L2 is β, 0°<β≤60°, the first section pipe extends along the axial direction of the ring-shaped distributor, and the third section pipe extends along the radial direction of the ring-shaped distributor.

[0009] In some embodiments, the first elbow pipe has a central angle of α, and 90°≤α≤150°.

[0010] In some embodiments, 20°≤β≤40°.

[0011] In some embodiments, the second elbow pipe has a central angle of γ,

[0012] In some embodiments, the first elbow pipe has an inner diameter of d1, and a bending radius of R1, and d1 / R1<1.

[0013] and / or,

[0014] the second elbow pipe has an inner diameter of d2, and a bending radius of R2, and d2 / R2<1.

[0015] In some embodiments,

[0016] The annular distributor comprises an outer ring wall, upper and lower ends of the outer ring wall are respectively provided with an annular upper cover plate and an annular upper bottom plate, the annular distributor is separately provided with an inner ring wall, or the shell constitutes the inner ring wall of the annular distributor, an annular space between the outer ring wall, the annular upper cover plate, the annular upper bottom plate and the inner ring wall is an annular distribution cavity, and the air suction port is located below the annular distribution cavity.

[0017] The annular distributor further comprises a fourth section pipe, the fourth section pipe extends upward and downward in the annular distributor, and an outlet of the fourth section pipe is communicated with the first section pipe through the air exhaust port.

[0018] The annular distribution cavity has a height of H1, the fourth section pipe has a height of H2, and 0.6≤H2 / H1≤0.9.

[0019] In some embodiments, the fourth section pipe is fixed on the inner ring wall or the outer ring wall through a fixing member.

[0020] In some embodiments, a distance between a top of the fixing member and the annular lower bottom plate is H3, and 0.5≤H3 / H2≤1.

[0021] In another aspect, the application further provides a compressor comprising the annular distributor, the compressor has a shell, and the annular distributor is sleeved on an outer wall surface of the shell.

[0022] Finally, the application provides an air conditioner comprising the compressor.

[0023] The application separates the exhaust port and the air inlet port in the circumferential direction of the compressor (the circumferential direction of the annular distributor), and extends the second section pipe along the tangential direction of the shell of the compressor, so that when the pressure pulsation generated by the pump body in the compressor is transmitted to the second section pipe, the second section pipe effectively damps the pressure pulsation. On the other hand, the prior art does not provide a second section pipe extending along the tangential direction of the shell of the compressor, and the pressure pulsation is distributed along the axial direction of the compressor, which is easy to cause the compressor to swing. The vibration of the pressure pulsation to the second section pipe of the application is distributed along the tangential direction of the shell of the compressor, and the vibration of the compressor generated by the pressure pulsation is difficult to cause the compressor to swing, which is beneficial to the vibration and noise reduction of the compressor. BRIEF DESCRIPTION OF DRAWINGS

[0024] In order to more clearly illustrate the embodiments of the application or the technical solutions in the prior art, the drawings needed to be used in the following embodiment or prior art description will be briefly introduced. The drawings in the following description are only exemplary, and those skilled in the art can also obtain other embodiment drawings according to the provided drawings without creative labor.

[0025] Figure 1 is a sectional view of the compressor of the embodiment of the application;

[0026] Figure 2 is a sectional view of the compressor of the embodiment of the application Figure 1 in the direction of B-B;

[0027] Figure 3 is a sectional view of the compressor of the embodiment of the application Figure 1 in the direction of C-C;

[0028] Figure 4 is a sectional view of the compressor of the embodiment of the application

[0029] Figure 5 is a schematic view in the direction of A of the compressor of the embodiment of the application Figure 4

[0030] Figure 6 is a sectional view of the compressor of the embodiment of the application

[0031] Figure 7 is an enlarged view of E in the compressor of the embodiment of the application Figure 6

[0032] Figure 8 is an oblique view of the compressor of the embodiment of the application

[0033] The reference signs are:

[0034] ​​1. compressor; 101. housing; 102. inlet pipe; 103. outlet pipe; 104. suction port; 2. ring distributor; 201. outer ring wall; 202. inner ring wall; 203. ring upper cover plate; 204. ring lower bottom plate; 205. outlet port; 206. ring distribution cavity; 3. suction pipe; 301. first section pipe; 302. second section pipe; 303. third section pipe; 304. fourth section pipe; 305. first elbow pipe; 306. second elbow pipe; 4. pump body; 5. motor; 6. oil return hole; 7. fixing member. DETAILED DESCRIPTION

[0035] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments of the present application. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0036] In the description of the present application, it should be understood that the orientation words such as "front, back, up, down, left, right", "transverse, vertical, perpendicular, horizontal" and "top, bottom" and the like indicate the orientation or position relationship shown in the drawings, which are only for the convenience of describing the present application and simplifying the description, and do not indicate and imply that the indicated device or element must have a specific orientation or be constructed and operated in a specific orientation, therefore it cannot be understood as a limitation on the scope of protection of the present application; the orientation words "inner, outer" refer to the inner and outer of the contour of each component itself.

[0037] For the convenience of description, spatial relative terms such as "over", "above", "upper surface", "upper" and the like can be used herein to describe the spatial position relationship of one device or feature with other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawings is inverted, the device described as "above" or "over" other devices or structures will be positioned "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below" orientations. The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein are interpreted accordingly.

[0038] In addition, it should be noted that the use of the terms "first", "second" and the like is merely intended to distinguish between similar objects, and does not have a special meaning, and therefore cannot be understood as a limitation on the scope of protection of the present application.

[0039] The ring-shaped distributor is set around the compressor, which not only reduces the size of the compressor, but also improves the noise of the compressor. The ring-shaped distributor becomes an important structure of the compressor. Since the distributor is more compact with the compressor shell, and the L-shaped pipeline is communicated with the suction port of the compressor at one end and is higher than the bottom of the ring-shaped distribution cavity of the ring-shaped distributor by a certain distance at the other end, thereby forming a liquid storage cavity at the bottom of the ring-shaped distribution cavity. Since the turning radius of the L-shaped pipeline is small, the flow resistance of the gas in the L-shaped pipeline is large, and the vibration generated by the pressure pulsation of the pump body entering the L-shaped pipeline propagates along the axial direction of the compressor, causing the compressor to swing greatly. In order to reduce the adverse effects of the pressure pulsation generated by the pump body on the compressor, the following solutions are disclosed.

[0040] In combination with Figures 1-8 As shown in the first aspect, the present application provides a ring-shaped distributor, which is sleeved on the outer shell 101 of the compressor 1, the outer shell 101 is provided with a suction port 104, the ring-shaped distributor 2 is provided with an exhaust port 205, the suction port 104 is located outside the ring-shaped distributor 2, the ring-shaped distributor 2 further comprises a suction pipe 3, the inlet end of the suction pipe 3 is communicated with the ring-shaped distributor 2 through the exhaust port 205, and the outlet end of the suction pipe 3 is communicated with the suction port 104.

[0041] The suction pipe 3 comprises a second section of pipe 302, and the second section of pipe 302 extends along the tangential direction of the outer shell 101.

[0042] Since the suction port 104 of the compressor 1 is directed to the radial direction of the housing, the pulsation generated by the pump body 4 in the compressor 1 during operation is discharged from the suction port 104 along the radial direction, and the second section pipe 302 extends along the tangential direction of the annular distributor 2, so that the direction of the pulsation transmission is changed, that is, the pulsation generated by the pump body 4 during operation is transmitted to the annular distributor cavity 206 along the suction pipe 3, and since the second section pipe 302 extends along the tangential direction of the annular distributor 2, the direction of the pressure pulsation (vibration) is changed when the pressure pulsation enters the second section pipe 302, and part of the vibration energy is absorbed by the second section pipe 302 when the direction of the pressure pulsation (vibration) is changed, so that the excitation effect of the pressure pulsation generated by the pump body 4 during operation on the vibration of the suction pipe 3 is effectively attenuated, and the vibration noise generated by the suction pipe 3 and the annular distributor 2 is reduced. Since the annular distributor 2 is sleeved on the compressor 1, the vibration of the compressor 1 is reduced, and the stability of the operation of the compressor 1 is improved. The tangential direction of the annular distributor 2 referred to herein is consistent with the tangential direction of the compressor 1, and the axial direction of the annular distributor 2 is also consistent with the axial direction of the compressor 1 (the cylindrical housing 101 of the compressor 1 is the axial direction of the compressor 1).

[0043] Specifically, the vibration of the suction pipe 3 is affected by two factors. First, the pressure pulsation generated by the cyclic operation of the pump body 4 is transmitted along the intake path. For the suction pipe 3 structure in the prior art that does not have a second section pipe 302 extending along the tangential direction of the compressor 1 (the first section pipe 301 and the third section pipe 303 are disclosed below, but the second section pipe 302 is used here for ease of explanation), the pulsation enters the first section pipe 301 from the third section pipe 303 and acts directly on the first section pipe 301. Since the first section pipe 301 extends along the axial direction of the annular distributor 2, the pressure pulsation propagates within the first section pipe 301, causing the first section pipe 301 to produce significant radial vibration. This radial vibration (the pressure pulsation generates radial vibration on the compressor 1 along the axial direction of the annular distributor 2, that is, it exerts force on different heights of the compressor 1 in the height direction of the compressor 1) causes the compressor 1 to sway as a whole. The upper end of the compressor 1 sways more than the lower end, which reduces the stability of the compressor 1. In this application, since the second section pipe 302 extends tangentially along the annular distributor 2, when the pressure pulsation is transmitted to the second section pipe 302, the pressure pulsation causes the second section pipe 302 to vibrate tangentially along the annular distributor 2 (the pressure pulsation generated by the pressure pulsation on the compressor 1 is distributed tangentially along the annular distributor 2, that is, it exerts force on different positions of the compressor 1 in the tangential direction of the compressor 1). Since the second section pipe 302 of this application extends tangentially along the compressor 1, the pressure pulsation is not only better attenuated in the second section pipe 302, but the attenuated pressure pulsation also causes a smaller swaying amplitude on the upper end of the compressor 1. The two ends of the second section pipe 302 are not directly fixed to the annular distributor 2 or the compressor 1, which increases the flexibility of the suction pipe 3 in the tangential direction (the second section pipe 302 is more prone to deformation when subjected to external force; the suction pipe 3 can be made of copper, utilizing the toughness of copper to absorb vibration), which is beneficial for absorbing the excitation energy transmitted to the second section pipe 302 by pressure pulsation, thus reducing the excitation effect of cylinder pressure pulsation on the vibration of the pump body 4 suction pipe. Second: The radial vibration of the distributor can be limited by the constraint of the suction pipe 3 (the suction pipe 3 has a reinforcing effect on the distributor). The second section pipe 302 of this application extends along the tangential direction of the compressor 1, basically consistent with the tangential direction, increasing the tangential stiffness, strengthening the constraint effect on the distributor, and reducing the radial vibration amplitude of the distributor.

[0044] Preferred, such as Figures 1-3 As shown, the suction pipe 3 further includes a first section pipe 301, a third section pipe 303, a first bend pipe 305, and a second bend pipe 306. The first section pipe 301 is connected to the annular liquid separator 2 via the exhaust port 205, and the third section pipe 303 is connected to the suction port 104. The first section pipe 301 and the second section pipe 302 are connected via the first bend pipe 305, and the second section pipe 302 and the third section pipe 303 are connected via the second bend pipe 306.

[0045] The suction pipe 3 is divided into at least three sections, and adjacent sections are connected by a bend, so that the flow resistance is further reduced as the gas flows from the distributor into the compressor 1.

[0046] Furthermore, the first section pipe 301, the second section pipe 302, and the third section pipe 303 are all straight pipes to minimize the flow resistance of the gas.

[0047] The first bend 305, the second bend 306, and the second section 302 can be integrally formed into a single component. The first bend 305 and the first section 301 can be welded together or fixed by insertion.

[0048] Preferred, such as Figures 1-3 , Figure 8 As shown, on the projection of the annular distributor 2 in the axial direction, the line connecting the center of the air inlet 104 and the center of the annular distributor 2 is L1, the line connecting the center of the air outlet 205 and the center of the annular distributor 2 is L2, the angle between L1 and L2 is β, 0°<β≤60°; the first section tube 301 extends along the axial direction of the annular distributor 2, and the third section tube 303 extends along the radial direction of the annular distributor 2.

[0049] The first section of pipe 301 extends along the axial direction of the annular distributor 2, facilitating the entry of gas from the annular distributor 2 into the suction pipe 3. A pump body 4 is installed inside the casing 101 of the compressor 1, with its inlet connected to the suction port 104. The third section of pipe 303 extends along the radial direction of the annular distributor 2, allowing it to directly connect to the inlet of the pump body 4 via the suction port 104. Furthermore, the first section of pipe 301 is vertically positioned for ease of installation and to accelerate the entry of gas into the suction pipe 3.

[0050] This application effectively reduces the gas flow resistance within the suction pipe 3 connecting the exhaust port 205 and the suction port 104 of the compressor 1 in the circumferential direction of the annular distributor 2 by distributing the exhaust port 205 and the suction port 104 of the compressor 1 in the axial direction of the annular distributor 2. Specifically, in the projection of the annular distributor 2 along its axial direction, the line connecting the center of the suction port 104 and the center of the annular distributor 2 is L1, and the line connecting the center of the exhaust port 205 and the center of the annular distributor 2 is L2. The angle between L1 and L2 is β, which is 0° < β ≤ 60°, compared to β = 0°. Since the first section 301 extends along the axial direction of the annular distributor 2, and the third section 303 extends along the radial direction of the annular distributor 2, the second section 302 is located between the first section 301 and the second section 303 in the circumferential direction of the annular distributor 2. This effectively reduces the gas flow path in the suction pipe 3 and minimizes the kinetic energy loss of the gas.

[0051] The suction port 104 is arranged outside the annular distributor 2, and the turning radius of the suction pipe 3 at the suction port 104 is larger, thereby enabling the gas entering the suction pipe 3 to have smaller resistance when entering the suction port 104 and smaller kinetic energy loss.

[0052] The fixing mode between the annular distributor 2 and the compressor 1 is welding, thereby ensuring the sealing performance; the suction port 104 is arranged outside the annular distributor 2, which is also beneficial to the welding fixing and sealing between the suction pipe 3 and the suction port 104, the residues generated by the welding between the suction pipe 3 and the suction port 104 cannot enter the inside of the distributor, which is beneficial to the cleaning of the inside of the annular distributor 2. The operation space during the welding between the suction pipe 3 and the suction port 104 is larger, which is beneficial to improving the production efficiency and product quality, and is also beneficial to the air tightness test. In specific production, the suction pipe 3 is first welded on the annular distributor 2, and then the annular distributor 2 is welded on the shell 101 of the compressor 1; so that the annular distributor 2 can be produced and manufactured as a separate component, which reduces the serial process of the compressor 1 manufacturing and improves the production efficiency of the compressor 1. Preferably, as shown in the drawings, the annular distributor 2 is first welded on the shell 101 of the compressor 1, and then the suction pipe 3 is welded on the annular distributor 2. Figure 7 As shown in the drawings, the central angle of the first elbow pipe 305 is α, and 90°≤α≤150°.

[0053] When α<90°, the first elbow pipe 305 generates larger resistance to the gas; when α>150°, in the axial direction of the annular distributor 2, the distance between the exhaust port 205 and the suction port 104 is too large, the height of the annular separation chamber 206 is smaller and the volume is smaller when the compressor 1 has the same height, which is not conducive to the gas-liquid separation. If the height of the annular distributor 2 needs to be higher than the height of the shell 101 of the compressor 1 in order to maintain the separation effect of the annular distributor 2, the height of the compressor 1 is too high, which affects the axial compactness of the compressor 1. The annular separation chamber 206 is a space for gas-liquid separation, which is specifically described below. The "height" in the present application refers to the distance between the top and the bottom when the compressor 1 is normally working. When the compressor 1 is normally working, the axis of the annular distributor 2 is vertically arranged.

[0054] In the range of 90°≤α≤150°, the larger α is, the smaller the resistance of the gas flowing through the first elbow pipe 305 is, and the smaller the annular separation chamber 206 is, but the volume of the annular separation chamber 206 is still within a reasonable range; the smaller α is, the larger the volume of the annular distributor 2 is, and the larger the resistance of the gas flowing through the first elbow pipe 305 is, and the flow resistance is also within a reasonable range; when the size of the annular separation chamber 206 of the annular distributor 2 is certain, the height of the annular separation can be lower, which is beneficial to lowering the gravity center of the compressor 1 and the stability of the operation of the compressor 1. The specific setting of α depends on the application place of the compressor 1 and the working condition in the place.

[0055] When α=90° and the first section pipe 301 is vertically arranged, the second section pipe 302 is horizontally arranged.

[0056] Preferably, as shown in the figure, 20°≤β≤40°. Figure 3

[0057] Too small β angle will limit the turning radius of the second elbow pipe 306, affecting the local resistance loss, too large β angle will cause the second section pipe 302 too large, affecting the resistance loss along the way.

[0058] When β < 20°, in order to reduce the gas flow resistance, the pipeline connected between the exhaust port 205 and the suction port 104 must extend to the radial outside of the annular distributor 2, increasing the overall radial size of the annular distributor 2, too large radial size increases the vibration amplitude of the compressor 1, which in turn will also cause noise increase. When β > 40°, the length of the second section pipe 302 is large, increasing the flow distance of the gas, reducing the flow velocity of the gas, which is not conducive to the compression performance of the compressor 1. Therefore, 20°≤β≤40° can avoid both the too large radial size of the annular distributor 2 and the too low velocity of the gas entering the inside of the compressor 1.

[0059] In addition, within 20°~40°, the length of the second section pipe 302 is also constrained, too large β will cause the second section pipe 302 too long, the overall stiffness of the suction pipe 3 is insufficient, and the reinforcement effect of the annular distributor 2 is weakened; too small β will cause the length of the suction pipe too short, the flexibility in the tangential direction is insufficient, which is not conducive to the tangential excitation energy attenuation of the pressure pulsation in the second section pipe 302. Reasonable β value can make the radial and tangential vibration of the suction pipe 3 and the distributor both achieve good reduction effect, thereby obtaining better noise reduction effect.

[0060] Preferably, as shown in the figure, the central angle of the second elbow pipe 306 is γ, Figure 2

[0061] In the range of 0°<γ≤90°, the smaller the γ, the smaller the resistance of the gas at the second elbow pipe 306, and the less the energy loss of the gas flow is changed; the pressure pulsation generated by the periodic operation of the pump body 4 also has less attenuation at the second elbow pipe 306, and the pressure pulsation enters the second section pipe 302 for attenuation, effectively reducing the vibration of the compressor 1. The larger the γ, the smaller the space occupied by the suction pipe 3, and the smaller the overall radial size of the compressor 1, which is conducive to the application of the compressor 1 in a smaller space. When γ < 0°, the space occupied by the suction pipe 3 is too much, and when γ > 90°, the resistance of the gas at the second elbow pipe 306 is too large.

[0062] ​​​​When the first section pipe 301, the drop section pipe and the third section pipe 303 are straight pipes, and the first section pipe 301 is vertically arranged (extending along the axial direction of the annular distributor 2), and the axis of the third section pipe 303 extends along the radial direction of the annular distributor 2, α and γ have a negative correlation, that is, the greater α is, the smaller γ is.

[0063] Preferably, the inner diameter of the first elbow pipe 305 is d1, and the bending radius of the first elbow pipe 305 is R1, and d1 / R1<1.

[0064] And / or,

[0065] The inner diameter of the second elbow pipe 306 is d2, and the bending radius of the second elbow pipe 306 is R2, and d2 / R2<1.

[0066] The axes of the first elbow pipe 305 and the second elbow pipe 306 are arcs, and according to the resistance loss coefficient of gas at the bending part of the pipe θ is the central angle of the elbow pipe, and the unit is radian, d is the inner diameter of the pipe, and R is the bending radius of the pipe. It can be seen that the resistance loss coefficient k at the bending part of the pipe decreases rapidly with the increase of the bending radius of the pipe. Since the air inlet 104 is arranged outside the annular distributor 2, the bending radius of the first elbow pipe 305 and the second elbow pipe 306 can be larger, so that d1 / R1<1 of the first elbow pipe 305 and d2 / R2<1 of the second elbow pipe 306 can be realized, thereby reducing the resistance of gas at the elbow pipe and ensuring the flow velocity of gas. The plurality of pipes are connected together by welding.

[0067] Preferably, as shown in Figure 1 , Figure 4 and Figure 6 The annular distributor 2 comprises an outer ring wall 201, and annular upper cover plates 203 and annular upper bottom plates are arranged at the upper and lower ends of the outer ring wall 201 respectively, the annular distributor 2 is provided with an inner ring wall 202, or the shell 101 constitutes the inner ring wall 202 of the annular distributor 2, and an annular space between the outer ring wall 201, the annular upper cover plates 203, the annular upper bottom plates and the inner ring wall 202 is an annular distribution cavity 206; the air inlet 104 is located below the annular distribution cavity 206.

[0068] The annular distributor 2 further comprises a fourth section pipe 304, the fourth section pipe 304 extends upward and downward in the annular distributor 2, and the outlet of the fourth section pipe 304 communicates with the first section pipe 301 through the air outlet 205.

[0069] The height of the annular distribution cavity 206 is H1, the height of the fourth section pipe 304 is H2, and 0.6≤H2 / H1≤0.9.

[0070] When H2 / H1<0.6, the liquid storage capacity of the annular distributor 2 is low, and the liquid will enter from the upper end inlet of the fourth section pipe 304; when H2 / H1>0.9, the upper end inlet of the fourth section pipe 304 is close to the top of the annular distributor 2, and the kinetic energy loss is large; through 0.6≤H2 / H1≤0.9, the annular distributor 2 obtains a larger liquid storage capacity and a smaller inflow resistance loss. That is, H2 / H1 is too small, which will result in too small liquid storage space, and H2 / H1 is too large, which will affect the flow field near the upper end inlet of the fourth section pipe 304, resulting in an increase in inflow resistance loss. The above setting range can make both aspects obtain better effects.

[0071] The lower end of the fourth section pipe 304 is provided with an oil return hole 6, which is close to the bottom wall of the annular distribution cavity 206. The distance from the oil return hole 6 to the bottom wall of the annular distribution cavity 206 can be set to 0.1H1, and the liquid in the annular distribution cavity 206 can flow back into the compressor 1 slowly from the oil return hole 6. The equivalent diameter of the oil return hole 6 is 1mm to 3mm, and the number of the oil return hole 6 is set to 1-2, so that the liquid (including liquid refrigerant and lubricating oil) in the annular distribution cavity 206 can flow back into the compressor 1 slowly under the suction force generated by the gas flow in the suction pipe 3, avoiding the rapid entry of a large amount of liquid into the compressor 1 to cause liquid hammer, and also avoiding the long-term operation of the compressor 1 in the absence of oil.

[0072] Preferably, as shown in Figure 1 The fourth section pipe 304 is fixed to the inner side ring wall 202 or the outer side ring wall 201 through a fixing member 7.

[0073] When the fourth section pipe 304 is fixed to the outer side ring wall 201, the β angle is larger, which can reduce the flow resistance of the gas flowing from the second section pipe 302 to the third section pipe 303 under the condition that the sizes of other structures remain unchanged.

[0074] When the annular distributor 2 is separately provided with the inner side ring wall 202, the fourth section pipe 304 fixed to the inner side ring wall 202 can absorb part of the vibration generated by the compressor 1, which is conducive to reducing the vibration and the noise generated thereby; similarly, when the outer shell of the compressor 1 constitutes the inner side ring wall 202, the annular distributor 2 is fixed to the outer shell 101 of the compressor 1 through the annular upper cover plate 203 and the annular lower bottom plate 204, and the fourth section pipe 304 is fixed to the outer shell 101 of the compressor 1, which not only can absorb the vibration generated by the compressor 1 to reduce the noise generated thereby, but also can improve the stiffness of the outer shell 101 of the compressor 1 to reduce the lateral shaking of the compressor 1 as a whole.

[0075] Further, the fourth section pipe 304 is a straight pipe, and the extending direction of the fourth section pipe 304 is consistent with the axial direction of the annular distributor 2. The fourth section pipe 304 being a straight pipe can reduce the flow resistance of the gas in the fourth section pipe 304, and increase the fitting degree when the fourth section pipe 304 is fixed to the outer ring wall 201, the inner ring wall 202 or the shell 101 of the compressor 1, so that the fixing is more firm.

[0076] Preferably, as shown in the figure, the distance between the top of the fixing member 7 and the annular lower bottom plate 204 is H3, and 0.5≤H3 / H2≤1. Figure 1

[0077] By 0.5≤H3 / H2≤1, the accuracy of the installation direction of the fourth section pipe 304 is ensured, the noise generated by the vibration of the fourth section pipe 304 in the annular distribution cavity 206 is reduced, and the vibration stress between the fourth section pipe 304 and the lower end of the annular cavity is reduced.

[0078] Further, the fourth section pipe 304 and the first section pipe 301 can be the same pipe, and the same pipe passes through the exhaust port 205 and is sealed with the exhaust port 205.

[0079] In a second aspect, the present application further provides a compressor, as shown in the figure, comprising the annular distributor, the compressor 1 has a shell 101, and the annular distributor 2 is sleeved on the outer wall surface of the shell 101. Figure 1

[0080] The annular distributor 2 is provided with an air inlet pipe 102, and when the compressor 1 works, the low-pressure refrigerant enters the annular distribution cavity 206 from the air inlet pipe 102. In the annular distribution cavity 206, due to the sudden drop of the flow rate and the change of the flow direction of the refrigerant, the liquid (liquid refrigerant and lubricating oil) included in the refrigerant is separated from the gas, the liquid is collected at the bottom of the annular distribution cavity 206, and the gas enters the pump body 4 assembly in the compressor 1 from the suction pipe 3. The motor 5 in the compressor 1 drives the pump body 4 assembly to work, so as to realize the compression and exhaust of the refrigerant. The high-temperature and high-pressure refrigerant is discharged from the compressor 1 through the exhaust pipe 103.

[0081] The compressor 1 can be a rolling piston compressor 1, a scroll compressor 1, a sliding vane compressor 1, a rotary cylinder compressor 1 and other types of positive displacement compressors 1.

[0082] In a third aspect, the present application provides an air conditioner comprising the above-mentioned compressor 1.

[0083] The air conditioner has smaller vibration and noise when working.

[0084] It is easy for those skilled in the art to understand that the advantageous technical features of the above-mentioned modes can be freely combined and superimposed without conflict. ​​

[0085] The above description is only the preferred embodiment of the present application, and is not used to limit the present application, any modification, equivalent replacement and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application. The above description is only the preferred embodiment of the present application, and it should be pointed out that, for ordinary skilled in the art, without departing from the technical principles of the present application, a number of improvements and variations can be made, and these improvements and variations should be considered as the protection scope of the present application.

Claims

1. A ring-shaped distributor, which is fitted on a casing (101) of a compressor (1), the casing (101) being provided with a suction port (104), the ring-shaped distributor (2) being provided with a discharge port (205), characterized in that, The suction port (104) is located outside the annular distributor (2), and the annular distributor (2) further comprises a suction pipe (3), an inlet end of the suction pipe (3) is communicated with the annular distributor (2) through the exhaust port (205), and an outlet end of the suction pipe (3) is communicated with the suction port (104); The suction pipe (3) comprises a second section pipe (302), and the second section pipe (302) extends along a tangential direction of the shell (101); The suction pipe (3) further comprises a first section pipe (301), a third section pipe (303), a first elbow pipe (305) and a second elbow pipe (306), the first section pipe (301) is communicated with the annular distributor (2) through the exhaust port (205), and the third section pipe (303) is communicated with the suction port (104); the first section pipe (301) and the second section pipe (302) are communicated through the first elbow pipe (305), and the second section pipe (302) and the third section pipe (303) are communicated through the second elbow pipe (306); In the projection of the annular distributor (2) in the axial direction, a line connecting the center of the suction port (104) and the center of the annular distributor (2) is L1, a line connecting the center of the exhaust port (205) and the center of the annular distributor (2) is L2, an included angle between L1 and L2 is β, 0°<β≤60°, the first section pipe (301) extends along the axial direction of the annular distributor (2), and the third section pipe (303) extends along the radial direction of the annular distributor (2); A central angle of the first elbow pipe (305) is α, and 90°≤α≤150°; The second bend (306) has a central angle of γ, .

2. The ring distributor of claim 1, wherein 20°≤β≤40°。 3. The ring distributor of claim 1, wherein, An inner diameter of the first elbow pipe (305) is d1, a bending radius of the first elbow pipe (305) is R1, and d1 / R1<1; And / or, An inner diameter of the second elbow pipe (306) is d2, a bending radius of the second elbow pipe (306) is R2, and d2 / R2<1.

4. The ring distributor of claim 1, wherein, The annular distributor (2) comprises an outer ring wall (201), and annular upper cover plates (203) and annular lower bottom plates (204) are arranged at upper and lower ends of the outer ring wall (201) respectively; The annular distributor (2) is separately provided with an inner ring wall (202), or the shell (101) constitutes the inner ring wall (202) of the annular distributor (2); An annular space between the outer ring wall (201), the annular upper cover plates (203), the annular upper bottom plates and the inner ring wall (202) is an annular distribution cavity (206), and the suction port (104) is located below the annular distribution cavity (206); The annular distributor (2) further comprises a fourth section pipe (304), the fourth section pipe (304) extends upward and downward in the annular distributor (2), and an outlet of the fourth section pipe (304) is communicated with the first section pipe (301) through the exhaust port (205). The height of the annular distributor cavity (206) is H1, the height of the fourth section pipe (304) is H2, and 0.6≤H2 / H1≤0.

9.

5. The ring distributor of claim 4, wherein, The fourth section pipe (304) is fixed on the inner side ring wall (202) or on the outer side ring wall (201) through a fixing member (7).

6. The ring distributor of claim 5, wherein, The distance between the top of the fixing member (7) and the annular lower bottom plate (204) is H3, and 0.5≤H3 / H2≤1.

7. A compressor characterized by, The compressor (1) comprises an outer shell (101), and the annular distributor (2) is sleeved on the outer wall surface of the outer shell (101).

8. An air conditioner characterized by comprising: The compressor (1) comprises the annular distributor (2) according to claim 7.

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