Rotary compressor and refrigeration equipment

Abstract

The rotary compressor comprises a shell, a motor assembly and a pump body assembly, the shell is provided with a first end and a second end in the first direction, the motor assembly comprises a stator and a rotor, and the pump body assembly is located on the side, close to the second end of the shell, of the motor assembly; the pump body assembly comprises an air cylinder, a roller, a bearing structure and a crankshaft, the inner diameter of the shell is D, the distance between the end face of the first end and the end face of the second end is H, the size of the stator in the first direction is T, the distance between the stator and the end face of the first end is H1, the distance between the stator and the bearing structure is H2, and the suction volume of the roller every time the roller rotates by a circle is V, the maximum rotating speed of the rotary compressor is Nmax, and the rotary compressor meets the following condition that D * D * H * T / ((V * Nmax) (H1 + H2)) is larger than or equal to 0.2 and smaller than or equal to 0.8. Therefore, the lubricating oil and the refrigerant in the shell can be fully separated under the conditions of small inner diameter and high rotating speed, and the lubricating oil is prevented from being discharged along with the refrigerant.

Description

Technical Field

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

[0002] Rotary compressors are core components in refrigeration and air conditioning systems, and their performance and reliability directly affect the energy efficiency, noise levels, and lifespan of the entire system. With market demands and the increasing installation requirements of refrigeration equipment, the miniaturization and high-speed operation of rotary compressors have become a clear technological development trend. However, in the process of miniaturization and high-speed operation of existing rotary compressors, the lubricating oil and refrigerant are prone to mixing during high-speed operation, resulting in an increase in the oil content in the exhaust gas. This affects heat transfer efficiency, increases system energy consumption, and leads to insufficient lubrication within the rotary compressor, exacerbating wear and affecting operational reliability and lifespan. Summary of the Invention

[0003] The main objective of this invention is to provide a rotary compressor and refrigeration equipment, which aims to improve the problem that existing rotary compressors, in the process of miniaturization and high speed, cannot separate lubricating oil and refrigerant within the casing, easily leading to the discharge of lubricating oil and refrigerant mixed together.

[0004] To achieve the above objectives, the rotary compressor proposed in this invention includes: A housing having a first end and a second end in a first direction; A motor assembly, disposed within the housing, the motor assembly including a stator and a rotor, the rotor being rotatably disposed about a first direction, the stator being sleeved around the outside of the rotor; and, A pump body assembly is disposed within the housing and located on the side of the motor assembly near the second end of the housing. The pump body assembly includes a cylinder, rollers, a bearing structure, and a crankshaft. The cylinder has an intake port and an exhaust port. The rollers are disposed within the cylinder. One end of the crankshaft is connected to the rotor, and the other end extends into the cylinder and is connected to the rollers. A section of the crankshaft is rotatably disposed within the bearing structure, and the bearing structure is fixedly disposed on the side of the cylinder facing the motor assembly. Wherein, the inner diameter of the housing is D, the distance between the end faces of the first end and the second end is H, the dimension of the stator in the first direction is T, the distance between the stator and the end face of the first end is H1, the distance between the stator and the bearing structure is H2, the suction volume per revolution of the roller is V, the maximum speed of the rotary compressor is Nmax, and the rotary compressor satisfies the following conditions: 0.2≤D×D×H×T / ((V×Nmax)(H1+H2))≤0.8.

[0005] In one embodiment, the inner diameter D of the housing satisfies: D < 100 mm.

[0006] In one embodiment, the maximum rotational speed Nmax of the rotary compressor satisfies: Nmax ≥ 120 rps.

[0007] In one embodiment, the distance H1 between the stator and the end face of the first end, and the distance H2 between the stator and the bearing structure satisfy: 0.2≤H2 / H1≤0.8.

[0008] In one embodiment, the suction volume V per revolution of the roller satisfies: 4cc ≤ V ≤ 11cc.

[0009] In one embodiment, the rotary compressor satisfies the following condition: 0.4≤D×D×H×T / ((V×Nmax)(H1+H2))≤0.7.

[0010] In one embodiment, the bearing structure includes: A flange, fixedly disposed within the housing; and, The bearing body is disposed on the flange and at least partially located in the inner ring of the flange, and the bearing body is sleeved around the crankshaft. Wherein, H2 is the distance between the stator and the flange.

[0011] In one embodiment, the flange is fixedly connected to the cylinder.

[0012] The present invention also proposes a refrigeration device, including the rotary compressor described above.

[0013] In one embodiment, the refrigeration equipment includes an air conditioner.

[0014] The technical solution of the present invention achieves sufficient separation of lubricating oil and refrigerant inside the housing by having the inner diameter of the housing as D, the distance between the end faces of the first end and the second end as H, the dimension of the stator in the first direction as T, the distance between the stator and the end face of the first end as H1, the distance between the stator and the bearing structure as H2, the suction volume of the roller per revolution as V, and the maximum speed of the rotary compressor as Nmax, when satisfying the following relationship: 0.2≤D×D×H×T / ((V×Nmax)(H1+H2))≤0.8. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0016] Figure 1 This is a schematic diagram of an embodiment of the rotary compressor provided by the present invention.

[0017] Explanation of icon numbers: 100. Rotary compressor; 1. Housing; 11. First end; 12. Second end; 2. Motor assembly; 21. Stator; 22. Rotor; 3. Pump body assembly; 31. Cylinder; 32. Roller; 33. Bearing structure; 331. Flange; 332. Bearing body; 34. Crankshaft.

[0018] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0019] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0020] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0021] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0022] This invention proposes a rotary compressor designed to address the problem that existing rotary compressors, in the process of miniaturization and high-speed operation, cannot separate lubricating oil and refrigerant within the casing, easily leading to the discharge of mixed lubricating oil and refrigerant.

[0023] Please see Figure 1 In one embodiment of the present invention, the rotary compressor 100 includes a housing 1, a motor assembly 2, and a pump assembly 3. The housing 1 has a first end 11 and a second end 12 in a first direction. The motor assembly 2 is disposed inside the housing 1 and includes a stator 21 and a rotor 22. The rotor 22 is rotatably disposed about the first direction, and the stator 21 is sleeved on the outside of the rotor 22. The pump assembly 3 is disposed inside the housing 1 and located on the side of the motor assembly 2 near the second end 12 of the housing 1. The pump assembly 3 includes a cylinder 31, rollers 32, a bearing structure 33, and a crankshaft 34. The cylinder 31 has an intake port and an exhaust port. The rollers 32 are disposed inside the cylinder 31. One end of the crankshaft 34 is connected to the rotor 22, and the other end extends into the... The cylinder 31 is connected to the roller 32, and a section of the crankshaft 34 is rotatably disposed within the bearing structure 33. The bearing structure 33 is fixedly disposed on the side of the cylinder 31 facing the motor assembly 2. The inner diameter of the housing 1 is D. The distance between the end face of the first end 11 and the end face of the second end 12 is H. The dimension of the stator 21 in the first direction is T. The distance between the stator 21 and the end face of the first end 11 is H1. The distance between the stator 21 and the bearing structure 33 is H2. The suction volume of the roller 32 per revolution is V. The maximum speed of the rotary compressor 100 is Nmax. The rotary compressor 100 satisfies the following condition: 0.2≤D×D×H×T / ((V×Nmax)(H1+H2))≤0.8.

[0024] It should be noted that in this invention, D×D×H is the product of the squares of the inner diameter of the housing 1 and the dimension of the housing 1 in the first direction, which indicates the packaged volume of the rotary compressor 100, that is, the theoretical minimum volume of the rotary compressor 100. This is then divided by the product of the volume drawn in per revolution of the roller 32 and the maximum rotational speed of the rotary compressor 100 (i.e., the roller 32) per unit time, V×Nmax. V×Nmax can be understood as the maximum volume of refrigerant that the rotary compressor 100 can theoretically handle per unit time, that is, the suction volume. V×Nmax represents the theoretical suction capacity (suction volume per unit time) of the rotary compressor 100 at its highest rotational speed, reflecting the theoretical upper limit of the rotary compressor 100's performance, thus obtaining the residence time characteristics of the refrigerant within the housing 1.

[0025] Furthermore, in this invention, the dimension T of the stator 21 in the first direction is divided by the distance between the end faces of the stator 21 and the first end 11 and the distance between the stator 21 and the bearing structure 33, plus H1+H2, where H1+H2 represents the distance that the lubricating oil needs to settle, to obtain the ratio of the dimension of the stator 21 in the first direction to the free space dimension in the first direction.

[0026] Therefore, in this invention, the relationship D×D×H×T / ((V×Nmax)(H1+H2)) can be equivalent to ((D×D×H) / (V×Nmax))×(T / (H1+H2)). This can represent the ratio of the residence time of the coolant in the housing 1 to the settling time of the lubricating oil. When this ratio is too large or too small, it is easy to cause the rotary compressor 100 to weaken its ability to separate the lubricating oil and the refrigerant or to have low energy efficiency. Therefore, when it is necessary to ensure the separation ability and energy efficiency of the rotary compressor 100 with small inner diameter and high speed, it is necessary to limit this ratio to a suitable range.

[0027] In the technical solution of this invention, when the rotary compressor 100 is working, the pump assembly 3 draws in refrigerant from the suction port. As the roller 32 rotates, the volume of the compression chamber in the cylinder 31 gradually decreases, and the refrigerant is compressed. When the compression chamber in the cylinder 31 is connected to the exhaust port, the compressed refrigerant is discharged from the exhaust port, thereby realizing a refrigeration cycle. Simultaneously, during the operation of the rotary compressor 100, lubricating oil is stored in the housing 1. The inner diameter of the housing 1 is D, and the distance between the end faces of the first end 11 and the second end 12 is H. The dimension of stator 21 in the first direction is T, the distance between the end face of stator 21 and the first end 11 is H1, the distance between stator 21 and bearing structure 33 is H2, the suction volume of roller 32 per revolution is V, and the maximum speed of rotary compressor 100 is Nmax. When the following relationship is satisfied: 0.2≤D×D×H×T / ((V×Nmax)(H1+H2))≤0.8, the rotary compressor 100 can achieve sufficient separation of lubricating oil and refrigerant in housing 1 under the conditions of small inner diameter and high speed, and avoid lubricating oil being discharged with refrigerant.

[0028] It is understood that D, H, T, H1 and H2 respectively indicate the geometric dimensions of the housing 1 and the stator 21, as well as the specific positional relationship between the stator 21 and the bearing structure 33 within the housing 1. In this invention, the units of D, H, T, H1 and H2 are all millimeters (mm).

[0029] Similarly, it is understood that V and Nmax represent the volume of refrigerant drawn in by the roller 32 in one revolution and the maximum rotational speed of the rotary compressor 100 per unit time, respectively. In this invention, the unit of V is cubic centimeters (cc) and the unit of Nmax is revolutions per second (rps).

[0030] Of course, in this invention, any parameter among D, H, T, H1, H2, V and Nmax can be adjusted to make the value calculated by the above relationship within its numerical range, thereby ensuring the separation performance of the rotary compressor 100 for lubricating oil and refrigerant.

[0031] It should be noted that when the inner diameter (D) of the housing 1 decreases, the energy efficiency of the rotary compressor 100 decreases. When the inner diameter of the housing 1 decreases to a value less than 0.2 calculated by the above formula, the oil level of the rotary compressor 100 deteriorates, which affects the separation ability of the rotary compressor 100 of lubricating oil and refrigerant, resulting in insufficient separation ability of the rotary compressor 100. When the inner diameter (D) of the housing 1 increases, the energy efficiency of the rotary compressor 100 increases. However, when the inner diameter of the housing 1 increases to a value greater than 0.8 calculated by the above formula, the oil discharge of the rotary compressor 100 increases, and the lubricating oil and coolant cannot be completely separated in the housing 1, causing the lubricating oil and coolant to be discharged from the housing 1 together, thereby affecting the heat transfer efficiency and aggravating the wear of the rotary compressor 100.

[0032] Specifically, in order to ensure the miniaturization of the rotary compressor 100 while ensuring that the energy efficiency of the rotary compressor 100 meets the corresponding requirements, in the embodiment of the present invention, the inner diameter D of the housing 1 satisfies: D < 100 mm.

[0033] It is understood that the present invention does not limit the specific value of the inner diameter of the housing 1. In the present invention, the inner diameter of the housing 1 can be set to any value within its corresponding range, as long as it is ensured that the selected value of the inner diameter of the housing 1 can meet the energy efficiency requirements of the rotary compressor 100, that is, the inner diameter value can be substituted into the above relationship so that its calculated value is within the corresponding range (0.2-0.8).

[0034] It should also be noted that when the distance (H) between the end face of the first end 11 and the end face of the second end 12 increases, the energy efficiency of the rotary compressor 100 increases. However, when the distance between the end face of the first end 11 and the end face of the second end 12 increases to a value greater than 0.8 calculated by the above formula, the oil level of the rotary compressor 100 deteriorates, which easily leads to the lubricating oil being discharged from the housing 1 along with the coolant, affecting the heat transfer efficiency and aggravating the wear of the rotary compressor 100. When the distance between the end face of the first end 11 and the end face of the second end 12 decreases, the oil discharge of the rotary compressor 100 increases until the distance between the end face of the first end 11 and the end face of the second end 12 decreases to a value less than 0.2 calculated by the above formula. In this case, the oil discharge of the rotary compressor 100 is too large, which also easily leads to the lubricating oil being discharged from the housing 1 along with the coolant. Therefore, in order to ensure that the rotary compressor 100 operates efficiently while achieving effective separation of lubricating oil and refrigerant, the distance H between the end face of the first end 11 and the end face of the second end 12 must be strictly controlled to satisfy the relationship 0.2≤DDHT / (V Nmax) / (H1+H2)≤0.8.

[0035] It should be further explained that when the dimension (T) of the stator 21 in the first direction increases, the energy efficiency of the rotary compressor 100 increases, but the oil discharge of the rotary compressor 100 deteriorates as the dimension of the stator 21 in the first direction increases. When the dimension of the stator 21 in the first direction increases to a value greater than 0.8 calculated by the above relationship, the oil discharge of the rotary compressor 100 deteriorates severely, and the rotary compressor 100 has insufficient ability to separate lubricating oil and refrigerant, which easily leads to lubricating oil being sprayed out of the housing 1. When the dimension of the stator 21 in the first direction decreases, the oil discharge of the rotary compressor 100 decreases.

[0036] Conversely, when the distance between the end face of the first end 11 and the end face of the second end 12 remains constant, and the distance (H1) between the stator 21 and the end face of the first end 11 increases, it indicates that the relative size of the stator 21 in the first direction decreases, and the oil discharge of the rotary compressor 100 decreases. When the distance between the stator 21 and the end face of the first end 11 decreases, it indicates that the relative size of the stator 21 in the first direction increases, and the oil discharge of the rotary compressor 100 increases. However, when the distance between the stator 21 and the end face of the first end 11 decreases to a value greater than 0.8 calculated by the above relationship, the oil discharge of the rotary compressor 100 is too large, and the lubricating oil is easily discharged from the housing 1 along with the coolant.

[0037] Similarly, when the distance (H2) between the stator 21 and the bearing structure increases, the oil discharge of the rotary compressor 100 decreases; when the distance between the stator 21 and the bearing structure 33 decreases, the oil discharge of the rotary compressor 100 increases, until the distance between the stator 21 and the bearing structure 33 decreases to a value greater than 0.8 calculated by the above relationship. This will affect the separation ability of the rotary compressor 100 of lubricating oil and refrigerant, resulting in insufficient separation ability of the rotary compressor 100.

[0038] Furthermore, in this invention, the distance (H1) between the stator 21 and the end face of the first end 11 and the distance (H2) between the stator 21 and the bearing structure 33 can also affect the noise of the rotary compressor 100. In this invention, if the ratio of H2 to H1 is too large or too small, the operating noise of the rotary compressor 100 will increase.

[0039] Specifically, in one embodiment of the present invention, in order to enable the rotary compressor 100 to operate at a low noise level, the distance (H1) between the end faces of the stator 21 and the first end 11, and the distance (H2) between the stator 21 and the bearing structure 33 satisfy: 0.2 ≤ H2 / H1 ≤ 0.8. This setting effectively controls the noise generated by the rotary compressor 100 during operation, avoiding noise problems caused by an excessively large or small ratio of H2 to H1.

[0040] In actual setup, by reasonably adjusting the values ​​of H1 and H2 to satisfy the above ratio, the operating noise of the rotary compressor 100 can be significantly reduced. This invention does not limit the specific ratio of H1 and H2, and can be selected according to the requirements in actual setup.

[0041] Furthermore, when the maximum speed (Nmax) of the rotary compressor 100 increases, the oil discharge of the rotary compressor 100 increases, and its oil sealing effect decreases. This continues until the maximum speed of the rotary compressor 100 increases to a value less than 0.2 calculated by the above formula. At this point, the oil level of the rotary compressor 100 deteriorates drastically, and the lubricating oil and refrigerant cannot be effectively separated within the housing 1. A large amount of lubricating oil will be discharged from the housing 1 along with the refrigerant. This not only severely reduces heat transfer efficiency and affects the cooling effect but also exacerbates the wear of the internal components of the rotary compressor 100, shortening its service life. When the maximum speed of the rotary compressor 100 decreases, the oil discharge of the rotary compressor 100 decreases, and its oil sealing effect increases. However, when the maximum speed of the rotary compressor 100 increases to a value greater than 0.8 calculated by the above formula, although the oil discharge problem of the rotary compressor 100 is somewhat alleviated, its overall performance will also decrease significantly, failing to meet normal cooling requirements.

[0042] Therefore, in order to ensure the working efficiency of the rotary compressor 100, in one embodiment of the present invention, the maximum speed (Nmax) of the rotary compressor 100 satisfies: Nmax≥120rps.

[0043] It is understood that the present invention does not limit the specific value of the maximum speed of the rotary compressor 100. In actual setting, it is only necessary to ensure that the selected value can meet the energy efficiency requirements of the rotary compressor 100, that is, the maximum speed can be substituted into the above relationship so that its calculated value is within the corresponding range (0.2-0.8).

[0044] To further ensure the energy efficiency requirements of the rotary compressor 100, in a further embodiment of the present invention, the suction volume (V) of the roller 32 per revolution satisfies: 4cc≤V≤11cc.

[0045] Similarly, the present invention does not limit the specific value of the suction volume per revolution of the roller 32; it can be selected according to the actual needs during actual setting.

[0046] It should be noted that this invention does not limit the specific values ​​obtained by the above-mentioned relational calculation. In this invention, by reasonably designing multiple parameters, the calculated value of the above-mentioned relational calculation can be any value within the corresponding range. In actual settings, it can be selected according to the requirements.

[0047] In a preferred embodiment of the present invention, the rotary compressor 100 satisfies the following condition: 0.4 ≤ D×D×H×T / ((V×Nmax)(H1+H2)) ≤ 0.7. This setting ensures both miniaturization and high speed of the rotary compressor 100 while further optimizing its energy efficiency and the separation performance of lubricating oil and refrigerant. When the calculated value of this relationship is within the more favorable range of 0.4 to 0.7, the lubricating oil and refrigerant can be more fully separated during operation of the rotary compressor 100, effectively preventing the lubricating oil from being discharged from the housing 1 along with the refrigerant. This reduces problems such as decreased heat transfer efficiency due to lubricating oil loss and increased wear of internal components of the rotary compressor 100, extending the compressor's service life and improving its operational stability and reliability.

[0048] Meanwhile, within this range, the rotary compressor 100 can better balance the needs of energy efficiency and miniaturization, achieving high working efficiency within a limited volume and meeting the performance requirements of refrigeration equipment in different application scenarios.

[0049] Furthermore, in this invention, since a portion of the crankshaft 34 is rotatably disposed within the bearing structure 33, to ensure the installation stability of the bearing structure 33 and further stabilize the rotation of the crankshaft 34, in one embodiment of this invention, the bearing structure 33 includes a flange 331 and a bearing body 332. The flange 331 is fixedly disposed within the housing 1, and the bearing body 332 is disposed within the flange 331, and at least partially located within the inner ring of the flange 331. The bearing body 332 is sleeved around the periphery of the crankshaft 34. With this arrangement, through the cooperation of the flange 331 and the bearing body 332, the flange 331 can provide stable and reliable support for the bearing body 332, and the bearing body 332 can ensure the smoothness of the crankshaft 34 during high-speed rotation, thereby reducing the wobbling of the crankshaft 34 and improving the overall performance and reliability of the rotary compressor 100.

[0050] It should be noted that, in this embodiment, the distance H2 between the stator 21 and the bearing structure 33 is actually the distance between the stator 21 and the flange 331.

[0051] Specifically, in one embodiment of the present invention, when the flange 331 is arranged in a planar manner with one end face of the stator 21 facing the first direction, the distance between the stator 21 and the flange 331 is the distance between the two end faces of the stator 21 and the flange 331 that are close to each other.

[0052] Please see Figure 1In another embodiment of the present invention, when the flange 331 is concave to one end face of the stator 21 in the first direction, the distance between the stator 21 and the flange 331 is the distance between the lowest point of the concave surface of the stator 21 and the flange 331.

[0053] In this way, the relative positional relationship between the stator 21 and the flange 331 can be determined according to the actual situation, thereby accurately determining the specific distance value between the stator 21 and the flange 331, and thus accurately determining the specific value of H2, so as to ensure the accuracy of the calculation results in the above relationship, and further ensure that the rotary compressor 100 can achieve efficient separation of lubricating oil and refrigerant in the housing 1 under the conditions of small inner diameter and high speed.

[0054] Of course, the present invention is not limited to which structural component the flange 331 is specifically connected to. The flange 331 can be fixedly connected to the housing 1 or fixedly connected to the cylinder 31. In actual installation, the appropriate option can be selected according to the requirements.

[0055] Specifically, in this embodiment, the flange 331 is fixedly connected to the cylinder 31.

[0056] Similarly, the specific connection form of the flange 331 and the cylinder 31 can also be selected according to the actual situation, and the present invention does not limit it.

[0057] Furthermore, the flange 331 further enhances the connection strength between the bearing body 332 and the cylinder 31, thereby further improving the structural stability of the rotary compressor 100.

[0058] The present invention also proposes a refrigeration device, which includes a rotary compressor 100. The specific structure of the rotary compressor 100 is as described in the above embodiments. Since the refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0059] The refrigeration equipment can be a refrigerator, an air conditioner, or a water dispenser, etc. In one specific embodiment, the refrigeration equipment includes an air conditioner. By designing the rotary compressor 100 of the air conditioner according to the above parameters, the rotary compressor 100 of the air conditioner can ultimately achieve sufficient separation of lubricating oil and refrigerant inside the housing 1 while meeting the requirements of small inner diameter and high speed, thus preventing the lubricating oil from being discharged with the refrigerant.

[0060] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A rotary compressor, characterized in that, include: A housing having a first end and a second end in a first direction; A motor assembly, disposed within the housing, the motor assembly including a stator and a rotor, the rotor being rotatably disposed about a first direction, the stator being sleeved around the outside of the rotor; and, A pump body assembly is disposed within the housing and located on the side of the motor assembly near the second end of the housing. The pump body assembly includes a cylinder, rollers, a bearing structure, and a crankshaft. The cylinder has an intake port and an exhaust port. The rollers are disposed within the cylinder. One end of the crankshaft is connected to the rotor, and the other end extends into the cylinder and is connected to the rollers. A section of the crankshaft is rotatably disposed within the bearing structure, and the bearing structure is fixedly disposed on the side of the cylinder facing the motor assembly. Wherein, the inner diameter of the housing is D, the distance between the end faces of the first end and the second end is H, the dimension of the stator in the first direction is T, the distance between the stator and the end face of the first end is H1, the distance between the stator and the bearing structure is H2, the suction volume per revolution of the roller is V, the maximum speed of the rotary compressor is Nmax, and the rotary compressor satisfies the following conditions: 0.2≤D×D×H×T / ((V×Nmax)(H1+H2))≤0.

8.

2. The rotary compressor as described in claim 1, characterized in that, The inner diameter D of the shell satisfies: D < 100 mm.

3. The rotary compressor as described in claim 1, characterized in that, The maximum speed Nmax of the rotary compressor satisfies: Nmax ≥ 120 rps.

4. The rotary compressor as described in claim 1, characterized in that, The distance H1 between the stator and the end face of the first end, and the distance H2 between the stator and the bearing structure, satisfy: 0.2≤H2 / H1≤0.

8.

5. The rotary compressor as described in claim 1, characterized in that, The suction volume V per revolution of the roller satisfies: 4cc ≤ V ≤ 11cc.

6. The rotary compressor as described in claim 1, characterized in that, The rotary compressor meets the following conditions: 0.4≤D×D×H×T / ((V×Nmax)(H1+H2))≤0.

7.

7. The rotary compressor as described in claim 1, characterized in that, The bearing structure includes: A flange, fixedly disposed within the housing; and, The bearing body is disposed on the flange and at least partially located in the inner ring of the flange, and the bearing body is sleeved around the crankshaft. Wherein, H2 is the distance between the stator and the flange.

8. The rotary compressor as described in claim 7, characterized in that, The flange is fixedly connected to the cylinder.

9. A refrigeration device, characterized in that, Including the rotary compressor as described in any one of claims 1 to 8.

10. The refrigeration equipment as described in claim 9, characterized in that, The refrigeration equipment includes an air conditioner.

Images