Compressor and refrigerating system

Abstract

The invention discloses a compressor and a refrigerating system. The compressor comprises a machine shell, a motor and a pump body assembly. The shell is provided with an accommodating cavity; the motor is installed in the containing cavity and comprises a rotor and a stator arranged on the periphery of the rotor in a sleeving mode. The pump body assembly is installed in the containing cavity and comprises a crankshaft, a static scroll plate, a movable scroll plate and a support, and the crankshaft sequentially penetrates through the rotor, the static scroll plate, the movable scroll plate and the support; wherein the torque coefficient K of motor stack output of unit displacement meets the relational expression: K = 2 * (V / T) 1 / 2 / D, V is the displacement of the compressor, T is the stack height of the stator, and D is the outer diameter of the stator. According to the scroll compressor, the problem that in the prior art, the output torque of a motor of a scroll compressor of a penetrating structure is insufficient or wasted can be solved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration, in particular to a compressor and a refrigeration system. BACKGROUND

[0002] The compressor is a core component of heat exchange equipment such as air conditioners and refrigerators, which is mainly divided into piston compressors, rotary compressors and scroll compressors. Among them, the scroll compressor is mainly composed of a motor, a crankshaft, a dynamic disc, a static disc, a cross slip ring and a main frame. The conventional scroll compressor is mainly divided into two types of pump body top and pump body bottom. The scroll compressor of the two types is provided with scroll teeth on one side of the dynamic disc base plate and a bearing part on the other side, and the crankshaft eccentric shaft is installed in the bearing part. The eccentric part of the crankshaft drives the dynamic disc to rotate and engages with the static disc to complete a series of processes such as suction, compression and exhaust.

[0003] At present, the commonly used scroll compressor is a through structure scroll compressor, and the crankshaft penetrates the dynamic disc and the static disc. However, in the working process of the existing scroll compressor, the motor output torque may be insufficient or wasted, which may adversely affect the performance of the scroll compressor. SUMMARY

[0004] The main purpose of the present application is to provide a compressor and a refrigeration system to solve the problem of insufficient or wasted motor output torque of the existing through structure scroll compressor.

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

[0006] A shell having a containing cavity;

[0007] A motor installed in the containing cavity, the motor comprising a rotor and a stator sleeved on the outer periphery of the rotor;

[0008] A pump body assembly installed in the containing cavity, the pump body assembly comprising a crankshaft, a static scroll disc, a dynamic scroll disc and a bracket, the crankshaft penetrating the rotor, the static scroll disc, the dynamic scroll disc and the bracket in sequence;

[0009] Wherein, the torque coefficient K of the unit displacement motor stack height output satisfies the relationship: K = 2 * (V / T) / D, V is the displacement of the compressor, T is the stack height of the stator, and D is the outer diameter of the stator. 1 / 2

[0010] Further, the torque coefficient K of the unit displacement motor stack height output satisfies the relationship: 0.32 ≤ K ≤ 0.62.

[0011] ​Further, a scroll tooth portion is arranged on the side of the orbiting scroll close to the fixed scroll, the height of the scroll tooth portion is H, and the thickness of the scroll tooth portion is t.

[0012] The volume coefficient M of the compressor satisfies the relationship: M=[H*H*2 / (t*D)]. 0.5 .

[0013] Further, the volume coefficient M of the compressor satisfies the relationship: 0.50≤M≤1.56.

[0014] Further, the height H of the scroll tooth portion satisfies the relationship: 7mm≤H≤18mm.

[0015] Further, the thickness t of the scroll tooth portion satisfies the relationship: 3mm≤t≤3.5mm.

[0016] Further, the outer diameter D of the stator satisfies the relationship: 85mm≤D≤114mm.

[0017] Further, the stack height T of the stator satisfies the relationship: 21mm≤T≤31.5mm.

[0018] Further, the displacement V of the compressor satisfies the relationship: 5000mm 3 ≤V≤16000mm 3 .

[0019] Further, the pump body assembly further comprises a cross slip ring arranged between the orbiting scroll and the bracket.

[0020] Further, the pump body assembly further comprises a soundproof cover arranged on the side of the fixed scroll away from the orbiting scroll, and the soundproof cover is provided with an air outlet hole.

[0021] Further, the compressor comprises a vertical compressor or a horizontal compressor.

[0022] In another aspect, the application further provides a refrigeration system comprising the above compressor.

[0023] By setting the torque coefficient K of the unit displacement motor stack height output, the stator stack height of the motor and the displacement of the compressor can be ensured to be within the best cost-effective range, thereby avoiding the situation of insufficient torque or waste of torque of the motor torque, effectively ensuring the reliability and stability of the compressor during operation, facilitating the miniaturization design of the compressor, and improving the cost performance of the compressor to a certain extent. BRIEF DESCRIPTION OF DRAWINGS

[0024] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments of this application and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings:

[0025] Figure 1 This is a cross-sectional view of the compressor disclosed in an embodiment of this application;

[0026] Figure 2 This is a front view of the motor and pump body assembly disclosed in the embodiments of this application;

[0027] Figure 3 This is a cross-sectional view of the pump body assembly disclosed in an embodiment of this application;

[0028] Figure 4 This is an exploded view of the pump body assembly (crankshaft removed) disclosed in the embodiments of this application.

[0029] The above figures include the following reference numerals:

[0030] 10. Housing; 101. Accommodating cavity; 20. Motor; 21. Rotor; 22. Stator; 30. Pump body assembly; 31. Crankshaft; 32. Stationary scroll plate; 33. Moving scroll plate; 331. Scroll teeth; 34. Bracket; 40. Cross slip ring; 50. Silencing cover; 60. Sealing ring. Detailed Implementation

[0031] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0032] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0033] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0034] As mentioned in the background section, existing scroll compressors often experience insufficient or wasted motor torque during operation. Therefore, the inventors of this application provide a novel compressor and have improved the dimensional relationships of components such as the pump body assembly to solve the problem of insufficient or wasted motor output torque in existing through-type scroll compressors. The compressor of this application will be described in detail below with reference to the accompanying drawings.

[0035] Combination Figures 1 to 4 As shown, according to an embodiment of this application, a compressor is provided, which includes a housing 10, a motor 20, and a pump assembly 30.

[0036] The housing 10 has a accommodating cavity 101; the motor 20 is installed within the accommodating cavity 101, and the motor 20 includes a rotor 21 and a stator 22 sleeved on the outer periphery of the rotor 21; the pump body assembly 30 is installed within the accommodating cavity 101, and the pump body assembly 30 includes a crankshaft 31, a stationary scroll plate 32, a moving scroll plate 33, and a bracket 34, with the crankshaft 31 passing sequentially through the rotor 21, the stationary scroll plate 32, the moving scroll plate 33, and the bracket 34; wherein, the torque coefficient K of the motor stack output per unit displacement satisfies the relationship: K=2*(V / T) 1 / 2 / D, V is the compressor displacement, T is the stack height of stator 22, and D is the outer diameter of stator 22. Figure 2 (The specific locations of T and D are shown).

[0037] Furthermore, in this embodiment, the torque coefficient K of the unit displacement motor stack height output satisfies the relationship: 0.32≤K≤0.62, for example 0.32, 0.36, 0.40, 0.44, 0.48, 0.52, 0.56, 0.60, 0.62 and any value between them.

[0038] In this application, when actually manufacturing the compressor, the motor 20 and the pump body assembly 30 can both be installed in the accommodating cavity 101, and the crankshaft 31 can be used to pass through the rotor 21, the stationary scroll plate 32, the moving scroll plate 33 and the bracket 34 in sequence to form a bottom-mounted installation of the pump body assembly 30. That is, the bracket 34 in the pump body assembly 30 is set on the side close to the bottom of the accommodating cavity 101, while the motor 20 is set on the side away from the bottom of the accommodating cavity 101. Because the crankshaft 31 has an oil supply channel located near the bottom of the accommodating cavity 101, and the oil level in the oil supply channel is used as a reference, the crankshaft 31 sequentially passes through the bracket 34, the moving scroll plate 33, the stationary scroll plate 32, and the bracket 34. When the pump body assembly 30 is installed in the bottom position as described in this application, the oil delivery distance of the oil supply channel can be shortened, allowing the lubricating oil to quickly reach the bearing of the pump body assembly 30 during startup or start-up, reducing the manufacturing cost of the pump body assembly 30 and the compressor, and facilitating the miniaturization and high-speed operation of the pump body assembly 30 and the compressor. Furthermore, since the crankshaft 31 sequentially passes through the rotor 21, the stationary scroll plate 32, the moving scroll plate 33, and the bracket 34, and the motor 20 is connected to the crankshaft 31 for driving, the pump body assembly 30 compresses the externally input refrigerant and discharges the refrigerant into the accommodating cavity 101, and then through the accommodating cavity 101 to the outside of the compressor, the structure is simple and the operation is convenient and quick. In other words, when the motor 20 drives the crankshaft 31 to rotate, it can drive the moving scroll 33 to rotate, thereby driving the stationary scroll 32 to rotate relative to the moving scroll 33, so as to realize the compression of the refrigerant inside the pump body assembly 30.

[0039] Meanwhile, by setting the torque coefficient K of the motor stack height per unit displacement, this application ensures that the stator 22 stack height of the motor 20 and the compressor displacement are within the optimal cost-performance range. This avoids insufficient torque or wasted torque in the motor 20, effectively guaranteeing the reliability and stability of the compressor during operation, and facilitating the miniaturization design of the compressor, thus improving the cost-performance ratio to a certain extent. K satisfies the relationship: K = 2*(V / T) 1 / 2 / D, and 0.32≤K≤0.62, for example 0.32, 0.36, 0.40, 0.44, 0.48, 0.52, 0.56, 0.60, 0.62 and any value in between. That is to say, the value of K will affect the torque of motor 20. When K is less than 0.32, the output torque of motor 20 will be excessive, increasing the consumption of electrical energy and increasing the size and weight of motor 20, thereby increasing the size of compressor and hindering the miniaturization of compressor. When K is greater than 0.62, the output torque of motor 20 will be insufficient, thus failing to drive pump body assembly 30 to rotate and failing to compress the refrigerant inside pump body assembly 30.

[0040] Furthermore, since the crankshaft 31 of the compressor in this application is mounted on the stationary scroll 32, the moving scroll 33, and the bracket 34, and the moving scroll 33 is located at the eccentric part of the crankshaft 31, when the crankshaft 31 rotates, the moving scroll 33 rotates synchronously with the eccentric part, and the moving scroll 33 is not easy to overturn. This reduces the noise and vibration of the pump body assembly 30 and the compressor to a certain extent, effectively ensuring the stable operation of the compressor and improving the reliability of the compressor.

[0041] Furthermore, in the actual installation of the pump body assembly 30, the bracket 34 or the stationary vortex disk 32 can be fixed to the inner wall of the accommodating cavity 101 by means of welding, fastener connection, etc., and the stationary vortex disk 32 can be fixedly installed on the bracket 34 by means of fastener connection.

[0042] Optionally, the fasteners in this application include fastening pins or screws, etc., and this application does not make specific limitations.

[0043] Further, see Figure 1 as well as Figures 3 to 4 As shown, in this embodiment, the moving scroll disk 33 is provided with a scroll tooth portion 331 on the side near the stationary scroll disk 32, wherein the height of the scroll tooth portion 331 is H, and the thickness of the scroll tooth portion 331 is t. Figure 3 (The specific locations of H and t are shown); the volumetric coefficient M of the compressor satisfies the following relationship: M=[H*H*2 / (t*D)] 0.5 Specifically, the volumetric coefficient M of the compressor satisfies the relationship: 0.50 ≤ M ≤ 1.56, for example, 0.5, 0.6, 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, 1.5, 1.56, and any value between them. In other words, by setting the volumetric coefficient M of the compressor, this application can ensure that the compressor has good performance and reliability, so that the refrigeration system can operate normally. When M is less than 0.5, the height and thickness of the scroll teeth 331 of the moving scroll 33 are reduced, thereby reducing the structural strength of the moving scroll 33. When the compressor is working, the moving scroll 33 is prone to deformation, leading to refrigerant leakage. When M is greater than 1.56, the height and thickness of the scroll teeth 331 of the moving scroll are increased, thereby increasing the space occupied by the scroll teeth 331 in the moving scroll 33, resulting in low area utilization of the moving scroll 33. At the same time, the outer diameter of the stator 22 is also increased, resulting in a larger overall size of the compressor.

[0044] Furthermore, in this embodiment, the height H of the scroll tooth section 331 satisfies the relationship: 7mm ≤ H ≤ 18mm, for example, 7mm, 8mm, 9mm, 10mm, 11mm, 12mm, 13mm, 14mm, 15mm, 16mm, 17mm, 18mm, and any value between them. The height of the scroll tooth section 331 has a significant impact on the suction volume of the scroll plate. When the height of the scroll tooth section 331 is less than 7mm, the suction volume of the moving scroll plate 33 is reduced, thereby affecting the performance of the compressor. When the height of the scroll tooth section 331 is greater than 18mm, the structural strength of the scroll tooth section 331 is reduced, and at the same time, the stress stability and operational stability of the moving scroll plate 33 are also reduced.

[0045] Furthermore, in this embodiment, the thickness t of the scroll tooth 331 satisfies the relationship: 3mm ≤ t ≤ 3.5mm, such as 3mm, 3.1mm, 3.2mm, 3.3mm, 3.4mm, 3.5mm, and any value between them. The thickness of the scroll tooth 331 affects its strength and rigidity. When the thickness of the scroll tooth 331 is less than 3mm, the moving scroll disk 33 is prone to deformation during operation, leading to refrigerant leakage, reducing the operational reliability of the moving scroll disk 33, thereby reducing the performance of the compressor and adversely affecting the refrigeration system. When the thickness of the scroll tooth 331 is greater than 3.5mm, the scroll tooth 331 occupies a large space on the scroll disk, resulting in a reduced area utilization rate of the moving scroll disk 33, which prevents better compression of the refrigerant and affects the performance of the compressor.

[0046] Furthermore, in this embodiment, the outer diameter D of the stator 22 satisfies the relationship: 85mm ≤ D ≤ 114mm, such as 85mm, 90mm, 95mm, 100mm, 105mm, 110mm, 114mm, and any value between them. The size of the outer diameter of the stator 22 will affect the performance of the motor 20. When the outer diameter of the stator 22 is less than 85mm, the stator 22 is prone to displacement during the high-speed rotation and vibration of the motor 20, affecting the performance and use of the motor 20, and in severe cases, causing safety accidents. At the same time, it may also lead to poor heat dissipation of the motor 20. When the outer diameter of the stator 22 is greater than 114mm, the excessively large outer diameter will increase the overall volume of the motor 20, thereby increasing the volume of the compressor, which is not conducive to the miniaturization design of the compressor. At the same time, it will also increase the manufacturing cost of the compressor and reduce the cost-effectiveness of the compressor.

[0047] Furthermore, in this embodiment, the stack height T of the stator 22 satisfies the relationship: 21mm ≤ T ≤ 31.5mm, such as 21mm, 23mm, 25mm, 27mm, 29mm, 31mm, 31.5mm, and any value between them. The size of the stack height of the stator 22 will affect the performance of the motor 20. When the stack height of the stator 22 is less than 21mm, the output torque of the motor 20 will be insufficient, which will prevent the motor 20 from driving the pump body assembly 30 to rotate, thus adversely affecting the performance of the compressor. At the same time, it is not conducive to the heat dissipation of the motor 20. When the stack height of the stator 22 is greater than 31.5mm, it will increase the overall size and weight of the motor 20, thereby increasing the size of the compressor, which is not conducive to the miniaturization design of the compressor, and to a certain extent increases the manufacturing cost of the compressor.

[0048] Furthermore, to meet the requirements of miniaturized scroll compressors, the compressor displacement V in this embodiment satisfies the following relationship: 5000mm² 3 ≤V≤16000mm 3 For example, 5000mm 3 7000mm 3 9000mm 3 11000mm 3 13000mm 3 15000mm 3 16000mm 3 And any values ​​between them. In this way, while ensuring the miniaturization of the scroll compressor, it also reduces displacement loss during the compressor compression process and improves the compressor's energy efficiency. When the compressor's displacement is less than 5000mm... 3 At this time, the pump body assembly 30 has limited suction capacity, which is not conducive to the operation of the compressor; when the compressor displacement is greater than 16000 mm³, 3 In this case, the weight or size of the compressor will increase significantly, which is not conducive to the miniaturization requirements of the compressor.

[0049] Further, see Figures 3 to 4 As shown, the pump body assembly 30 in this embodiment also includes a cross slip ring 40, which is disposed between the moving scroll plate 33 and the bracket 34. This arrangement facilitates the limiting of the moving scroll plate 33. Furthermore, to facilitate sealing the gap between the bracket 34 and the moving scroll plate 33, this application provides a sealing ring 60 between the moving scroll plate 33 and the bracket 34 (e.g., Figure 4 (As shown). After assembling the pump body assembly 30, as shown... Figure 3As shown, the sealing ring 60 is located in the groove of the bracket 34, and the top surface of the sealing ring 60 is in contact with the moving scroll plate 33. The outer side of the sealing ring 60 is in contact with the side wall of the groove. With this arrangement, when the pump assembly starts to work, the inner side of the sealing ring 60 near the crankshaft 31 is a high-pressure gas space, and the outer side of the sealing ring 60 away from the crankshaft is a medium-pressure gas that is drained out during the gas compression process.

[0050] Optionally, in other embodiments of this application, the cross slip ring 40 can also be set as a spherical coupling or a cylindrical pin coupling, etc. Any other variation under the concept of this application is within the protection scope of this application.

[0051] Further, see Figures 1 to 3 As shown, the pump assembly 30 in this embodiment also includes a silencer 50, which covers the side of the stationary scroll 32 opposite to the moving scroll 33. The silencer 50 has an air outlet (not shown in the figure). The silencer 50 is used to silence the refrigerant. Specifically, after the refrigerant is compressed by the moving scroll 33 and the stationary scroll 32, it is discharged from the stationary scroll 32 and then enters the silencer 50. The silencer 50 silences the refrigerant before it is discharged into the accommodating cavity 101, and finally discharged from the accommodating cavity 101 to the outside of the compressor.

[0052] Furthermore, the compressor in this embodiment includes a vertical compressor or a horizontal compressor. That is to say, the compressor in this application can be a vertical compressor or a horizontal compressor; this application does not specifically limit it. (The appendix to this embodiment is missing.) Figure 1 The diagram shows the case when the compressor is a vertical compressor. In a horizontal compressor, the oil level is not used as a reference, but the crankshaft 31 still passes through the rotor 21, the stationary scroll 32, the moving scroll 33, and the support 34 in sequence.

[0053] The compressor of this application will be described in detail below with reference to specific embodiments.

[0054] Example 1

[0055] See Figure 1 As shown, the compressor in this embodiment includes a housing 10, a motor 20, and a pump assembly 30. Both the motor 20 and the pump assembly 30 are installed within the accommodating cavity 101. The motor 20 includes a rotor 21 and a stator 22 sleeved around the outer periphery of the rotor 21. The pump assembly 30 includes a crankshaft 31, a stationary scroll plate 32, a moving scroll plate 33, and a bracket 34. The crankshaft 31 passes sequentially through the rotor 21, the stationary scroll plate 32, the moving scroll plate 33, and the bracket 34. The torque coefficient K of the motor stack output per unit displacement satisfies the following relationship: K = 2*(V / T). 1 / 2 / D, V is the compressor displacement, T is the stack height of stator 22, and D is the outer diameter of stator 22; the compressor's volumetric coefficient M satisfies the following formula: M=[H*H*2 / (t*D)] 0.5 H is the height of the vortex tooth section 331, and t is the thickness of the vortex tooth section 331.

[0056] In the actual machining of this compressor, the compressor is machined according to the following dimensional data. Specifically, the thickness of the scroll teeth 331 of the moving scroll 33 is 3mm, and the height is 7mm; the outer diameter of the stator 22 is 89mm, and the stack height of the stator 22 is 21mm; the compressor displacement is 5000mm³. 3 In this way, the torque coefficient of the motor with a unit displacement can be stacked to 0.39, and the volume coefficient of the compressor can be 0.61.

[0057] Example 2

[0058] Unlike Embodiment 1, in this embodiment, the thickness of the scroll teeth 331 of the moving scroll disk 33 is 3.2 mm and the height is 12 mm; the outer diameter of the stator 22 is 100 mm and the stacking height of the stator 22 is 26 mm; the compressor displacement is 10000 mm³ / h. 3 In this way, the torque coefficient of the motor with a unit displacement can be stacked to 0.39, and the volume coefficient of the compressor can be 0.95.

[0059] Example 3

[0060] Unlike Embodiment 1, in this embodiment, the thickness of the scroll teeth 331 of the moving scroll disk 33 is 3.5 mm and the height is 18 mm; the outer diameter of the stator 22 is 110 mm and the stack height of the stator 22 is 30 mm; the compressor displacement is 16000 mm³ / h. 3 In this way, the torque coefficient of the motor with a unit displacement can be stacked to 0.42, and the volume coefficient of the compressor can be 1.3.

[0061] Comparative Example 1

[0062] A compressor is provided as a comparative example, which differs from the compressor of Embodiment 1 in that: the thickness of the scroll teeth 331 of the moving scroll 33 is 5.5 mm and the height is 8 mm; the outer diameter of the stator 22 is 139 mm and the stack height of the stator 22 is 35 mm; and the compressor displacement is 8000 mm³ / h. 3 In this way, the torque coefficient of the motor with a unit displacement can be 0.22 and the volume coefficient of the compressor can be 0.41.

[0063] Comparative Example 2

[0064] The compressor differs from the compressor in Embodiment 1 in that: the thickness of the scroll teeth 331 of the moving scroll 33 is 5mm and the height is 6mm; the outer diameter of the stator 22 is 100mm and the stacking height of the stator 22 is 28mm; and the compressor displacement is 5000mm. 3 In this way, the torque coefficient of the motor with a unit displacement can be stacked to 0.27, and the volume coefficient of the compressor can be 0.38.

[0065] Comparative Example 3

[0066] The compressor differs from the compressor in Embodiment 1 in that: the thickness of the scroll teeth 331 of the moving scroll 33 is 3.2 mm and the height is 25 mm; the outer diameter of the stator 22 is 80 mm and the stacking height of the stator 22 is 20 mm; and the compressor displacement is 25000 mm³ / h. 3 In this way, the torque coefficient of the motor with a unit displacement can be stacked to 0.88, and the volume coefficient of the compressor can be 2.21.

[0067] Comparative Example 4

[0068] The compressor differs from the compressor in Embodiment 1 in that: the thickness of the scroll teeth 331 of the moving scroll 33 is 3mm and the height is 20mm; the outer diameter of the stator 22 is 85mm and the stacking height of the stator 22 is 21mm; and the compressor displacement is 16000mm³. 3 In this way, the torque coefficient of the motor with a unit displacement can be stacked to 0.65, and the volume coefficient of the compressor can be 1.77.

[0069] Table 1 shows the data on motor output torque and whether the volumetric coefficient enables the air conditioner to achieve optimal operating conditions.

[0070]

[0071]

[0072] As shown in Table 1, when the thickness of the scroll tooth portion 331 of the moving scroll disk 33 of the compressor of this application is 3mm to 3.5mm, the height of the scroll tooth portion 331 is 7mm to 18mm, the outer diameter of the stator 22 is 85mm to 114mm, the stack height of the stator 22 is 21mm to 31.5mm, and the compressor displacement is 5000mm... 3 Up to 16000mm 3This allows for a torque coefficient of 0.32 to 0.62 for the motor's output per unit displacement and a volumetric coefficient of 0.5 to 1.56 for the compressor. This avoids situations where the motor's torque is insufficient or wasted, effectively ensuring the reliability and stability of the compressor during operation. It also facilitates the miniaturization of the compressor, improving its cost-effectiveness to some extent. Furthermore, it ensures the compressor maintains good performance and reliability, guaranteeing the normal operation of the refrigeration system.

[0073] In summary, the compressor of this application has the following advantages:

[0074] (1) By setting the torque coefficient of the stacked output of the motor per unit displacement, this application can avoid insufficient torque or wasted torque of the motor, effectively ensure the reliability and stability of the compressor during operation, and facilitate the miniaturization design of the compressor, thereby improving the cost performance of the compressor to a certain extent.

[0075] (2) By setting the volume coefficient of the compressor, this application can ensure that the compressor has good performance and reliability, so as to ensure the normal operation of the refrigeration system;

[0076] (3) The pump body assembly of the compressor in this application is located on the side of the compressor close to the oil sump, and the motor is located on the side of the compressor away from the oil sump. The pump body assembly is in contact with the oil sump, which can shorten the oiling time when the compressor starts and improve the lubrication effect of the pump body assembly.

[0077] (4) The crankshaft of this application runs through the stationary scroll, the moving scroll and the support. The moving scroll is not easy to overturn when it rotates, which can reduce the vibration and noise of the compressor during operation.

[0078] (5) In this application, the stationary scroll plate is on the side of the moving scroll plate away from the oil sump, making the exhaust passage smoother and improving the compressor's energy efficiency.

[0079] On the other hand, embodiments of this application also provide a refrigeration system including the aforementioned compressor, thus encompassing all the technical effects of the compressor. Since the technical effects of the compressor have already been described in detail above, they will not be repeated here.

[0080] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0081] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0082] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A compressor, characterized in that, include: Housing (10), the housing (10) having an accommodating cavity (101); The motor (20) is installed in the accommodating cavity (101), and the motor (20) includes a rotor (21) and a stator (22) sleeved on the outer periphery of the rotor (21); A pump body assembly (30) is installed in the accommodating cavity (101). The pump body assembly (30) includes a crankshaft (31), a stationary scroll plate (32), a moving scroll plate (33), and a bracket (34). The crankshaft (31) passes sequentially through the rotor (21), the stationary scroll plate (32), the moving scroll plate (33), and the bracket (34). The torque coefficient K of the unit displacement motor stack height output satisfies the following relationship: K=2*(V / T) 1 / 2 / D, V is the displacement of the compressor, T is the stack height of the stator (22), and D is the outer diameter of the stator (22).

2. The compressor according to claim 1, characterized in that, The torque coefficient K of the unit displacement motor stack height output satisfies the following relationship: 0.32≤K≤0.

62.

3. The compressor according to claim 1, characterized in that, The moving scroll disk (33) is provided with a scroll tooth (331) on the side near the stationary scroll disk (32). The height of the scroll tooth (331) is H and the thickness of the scroll tooth (331) is t. The volumetric coefficient M of the compressor satisfies the following formula: M=[H*H*2 / (t*D)] 0.5 .

4. The compressor according to claim 3, characterized in that, The volumetric coefficient M of the compressor satisfies the following relationship: 0.50≤M≤1.

56.

5. The compressor according to claim 3, characterized in that, The height H of the vortex tooth (331) satisfies the following relationship: 7mm≤H≤18mm.

6. The compressor according to claim 3, characterized in that, The thickness t of the vortex tooth (331) satisfies the following relationship: 3mm≤t≤3.5mm.

7. The compressor according to any one of claims 1 to 4, characterized in that, The outer diameter D of the stator (22) satisfies the following relationship: 85mm≤D≤114mm.

8. The compressor according to any one of claims 1 to 4, characterized in that, The stacking height T of the stator (22) satisfies the following relationship: 21mm≤T≤31.5mm.

9. The compressor according to any one of claims 1 to 4, characterized in that, The displacement V of the compressor satisfies the following relationship: 5000mm 3 ≤V≤16000mm 3 .

10. The compressor according to claim 1, characterized in that, The pump body assembly (30) also includes a cross slip ring (40), which is disposed between the moving scroll plate (33) and the bracket (34).

11. The compressor according to claim 1, characterized in that, The pump body assembly (30) also includes a silencer cover (50), which is located on the side of the stationary scroll plate (32) away from the moving scroll plate (33), and the silencer cover (50) is provided with an air outlet.

12. The compressor according to claim 1, characterized in that, The compressor may be a vertical compressor or a horizontal compressor.

13. A refrigeration system, characterized in that, The refrigeration system includes the compressor according to any one of claims 1 to 12.

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