Cylinder block, cylinder assembly, rotary compressor, outdoor unit and air conditioner

Abstract

This disclosure relates to a cylinder block, cylinder assembly, rolling rotor compressor, outdoor unit, and air conditioner. The cylinder block is used for the rolling rotor compressor and has a mounting cavity, a vane slot, an intake port, and an exhaust port. The mounting cavity accommodates the rotor. The vane slot is located between the intake port and the exhaust port and is used to mount vanes. The vane slot is parallel to the centerline of the mounting cavity and has a first reference surface offset from the centerline of the mounting cavity. The first reference surface is located at the center of the width direction of the vane slot and is located on the side of the centerline of the mounting cavity closer to the intake port. Through the above technical solution, the cylinder block provided by this disclosure can reduce or even avoid the risk of vanes detaching from the rotor, thereby solving the problem of abnormal noise in the air conditioner. It also helps to reduce the clearance volume of, for example, the rolling rotor compressor and improve the volumetric efficiency of the rolling rotor compressor.

Description

Technical Field

[0001] This disclosure relates to the field of air conditioning technology, specifically to a cylinder block, cylinder assembly, rolling rotor compressor, outdoor unit, and air conditioner. Background Technology

[0002] In related technologies, after the compressor of an air conditioner finishes its exhaust process, a high-pressure medium may impact the contact area between the vane and the rotor within the exhaust sealed volume. When the impact force of the high-pressure medium on the contact area between the vane and the rotor is greater than the clamping force that presses the vane onto the rotor, the vane will detach from the rotor and then impact the rotor again, thus producing an abnormal noise. Utility Model Content

[0003] The purpose of this disclosure is to provide a cylinder block, cylinder assembly, rolling rotor compressor, outdoor unit, and air conditioner that can reduce or even avoid the risk of vanes detaching from the rotor, thereby solving the problem of abnormal noise in the air conditioner.

[0004] To achieve the above objectives, a first aspect of this disclosure provides a cylinder body for a rolling rotor compressor, the cylinder body having a mounting cavity, a vane groove, an intake port, and an exhaust port, the mounting cavity for accommodating a rotor, the vane groove being located between the intake port and the exhaust port and for arranging vanes, the vane groove being parallel to the centerline of the mounting cavity, the vane groove having a first reference surface offset from the centerline of the mounting cavity, the first reference surface being located at the center position in the width direction of the vane groove and located on the side of the centerline of the mounting cavity closer to the intake port.

[0005] Optionally, the slide groove has a first sidewall and a second sidewall opposite to each other, the first sidewall being located on the side of the second sidewall closer to the air inlet, the first reference surface being parallel to the first sidewall and the second sidewall and located at the center between the first sidewall and the second sidewall; the centerline of the mounting cavity is located between the first reference surface and the second sidewall.

[0006] Optionally, the cylinder has a shaft hole through which a shaft connected to the rotor passes, the centerline of the shaft hole coinciding with the centerline of the mounting cavity.

[0007] A second aspect of this disclosure provides a cylinder assembly including a rotor, a vane, and the cylinder block provided in the first aspect above.

[0008] Optionally, the slide has an end face that contacts the rotor, and the end face is arranged asymmetrically about the first reference plane.

[0009] Optionally, a working cavity is formed between the rotor and the inner wall of the mounting cavity. The slide has an end face that contacts the rotor. The end face includes a first guide surface and a second guide surface. The first guide surface is close to the intake port, and the second guide surface is close to the exhaust port. The connection between the first guide surface and the second guide surface contacts the rotor when the volume of the working cavity is at its maximum.

[0010] Optionally, the first guide surface and the second guide surface are configured such that the cut surface tangent to the connection is perpendicular to the first reference surface.

[0011] Optionally, the area of ​​the first guide surface is larger than the area of ​​the second guide surface.

[0012] Optionally, the first guide surface and / or the second guide surface are curved surfaces.

[0013] Optionally, the radius of the arc of the first guide surface is greater than the radius of the arc of the second guide surface.

[0014] Optionally, the radius of the arc of the first guide surface is 3mm-8mm; and / or, the radius of the arc of the second guide surface is 2.5mm-5mm.

[0015] Optionally, the slide has opposing third and fourth sidewalls, the third sidewall being close to the intake port and the fourth sidewall being close to the exhaust port, and the distance between the connection point of the first guide surface and the second guide surface and the third sidewall is greater than the distance between the connection point and the fourth sidewall.

[0016] A third aspect of this disclosure provides a rolling rotor compressor, including the cylinder assembly provided in the second aspect above.

[0017] A fourth aspect of this disclosure provides an outdoor unit comprising the rolling rotor compressor provided in the third aspect above.

[0018] The fifth aspect of this disclosure provides an air conditioner including the outdoor unit provided in the fourth aspect above.

[0019] Through the above-described technical solution, namely the cylinder body provided in this disclosure, the sliding vane groove on the cylinder body is constructed to be parallel to the center line of the mounting cavity and has a first reference surface that is offset from the center line of the mounting cavity. The first reference surface is located at the center of the width direction of the sliding vane groove and is arranged on the side of the center line of the mounting cavity near the intake port. That is, it can be understood that by offsetting the sliding vane groove on the cylinder body towards the intake port side, this disclosure increases the pressure-bearing area of ​​the sliding vane on the intake port side and decreases the pressure-bearing area of ​​the sliding vane on the exhaust port side. This reduces the thrust that pushes the sliding vane away from the rotor and increases the clamping force of the sliding vane pressing against the rotor. Therefore, when the high-pressure medium in the exhaust sealed volume impacts the contact area between the sliding vane and the rotor after the compressor exhaust process, for example, a higher impact force is required to impact the contact area between the sliding vane and the rotor to separate the sliding vane from the rotor compared to related technologies. Therefore, the cylinder body provided in this disclosure can reduce or even avoid the risk of the sliding vane separating from the rotor, thereby solving the problem of abnormal noise in the air conditioner.

[0020] Furthermore, since this disclosure increases the pressure-bearing area of ​​the vane on the intake side by shifting the vane groove on the cylinder block toward the intake side, and decreases the pressure-bearing area of ​​the vane on the exhaust side, it is also possible to reduce the volume occupied by the vane in the compression chamber (the closed space formed on the exhaust side) after the compressor exhaust process, for example, after the compressor exhaust process is completed. This helps to reduce the clearance volume of, for example, the rolling rotor compressor and improve the volumetric efficiency of the rolling rotor compressor.

[0021] Other features and advantages of this disclosure will be described in detail in the following detailed description section. Attached Figure Description

[0022] The accompanying drawings are provided to further illustrate the present disclosure and form part of the specification. They are used together with the following detailed description to explain the present disclosure, but do not constitute a limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the structure of the cylinder assembly provided in an exemplary embodiment of this disclosure; Figure 2 This is a schematic diagram of the cylinder assembly after the end cap has been removed, provided in an exemplary embodiment of this disclosure; Figure 3 This is a schematic diagram of the cylinder assembly after the end cap has been removed, provided in an exemplary embodiment of this disclosure, at another angle, where the rotor is at a rotation angle of 0° (the working chamber has the largest volume at this position). Figure 4 yes Figure 3 A schematic diagram of the structure after the central rotor rotates counterclockwise (in the direction of the arrow) to another angle, where the compressor's exhaust process ends when the rotor rotates to this position; Figure 5 This is a schematic diagram of the cylinder body of the cylinder assembly provided in an exemplary embodiment of this disclosure; Figure 6 This is a schematic diagram of the structure of the sliding vane of the cylinder assembly provided in an exemplary embodiment of this disclosure; Figure 7 This is a schematic diagram of the cylinder assembly after the end cap has been removed, as provided in the relevant technology.

[0023] Explanation of reference numerals in the attached figures 1-Cylinder block; 110-Mounting cavity; 120-Sliding vane groove; 121-First reference surface; 122-First side wall; 123-Second side wall; 130-Intake port; 140-Exhaust port; 150-Shaft hole; 2-Sliding vane; 210-End face; 211-First guide surface; 212-Second guide surface; 220-Third side wall; 230-Fourth side wall; 3-Rotor; 4-Second reference surface; 5-Shaft; 6-Working cavity; 7-Cut surface; 8-End cover; 9-Spring. Detailed Implementation

[0024] The specific embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit this disclosure.

[0025] In this disclosure, unless otherwise stated, "inner" and "outer" refer to the inner and outer contours relative to the outline of the component or structure itself. Furthermore, it should be noted that terms such as "first" and "second" are used to distinguish one element from another and do not indicate sequence or importance. Additionally, in the description with reference to the accompanying drawings, the same reference numerals in different drawings denote the same elements.

[0026] In related technologies, under operating conditions such as low load and low speed (e.g., 8Hz-10Hz), such as Figure 7 As shown, since the vane groove 120 and vane 2 are usually symmetrical, the bearing area of ​​vane 2 on the intake port 130 side is equal to the bearing area of ​​vane 2 on the exhaust port 140 side. This results in a smaller clamping force on vane 2 against rotor 3 under the action of internal and external pressure difference. That is, it can be understood that vane 2 will usually experience a resultant force F1 of the elastic force of the elastic element (e.g., spring 9) plus the rated exhaust pressure of the rolling rotor compressor (refer to...). Figure 6 Under the force (as shown), the sliding vane 2 is pressed against the rotor 3. Additionally, as the rotor 3 rotates and compresses the medium (e.g., refrigerant), the sliding vane 2 experiences a thrust F2 at the suction port 130 (refer to...). Figure 6 The forces acting on the slider 2 shown are illustrated, and the slider 2 will also experience a thrust F3 on the exhaust port 140 side (refer to...). Figure 6As shown in the diagram, the pressure inside the compression chamber (the enclosed space formed by the exhaust port 140) on the exhaust port 140 side is usually greater than the rated intake pressure and rated exhaust pressure on the intake port 130 side as the rotor 3 rotates and compresses the medium (e.g., refrigerant). That is, the pressure inside the compression chamber will vary between 1.2-1.8 times (e.g., 1.3 times) of the rated intake pressure or 1.2-1.8 times (e.g., 1.3 times) of the rated exhaust pressure as the rotor 3 rotates and compresses the medium (e.g., refrigerant). In summary, under conditions such as low load and low speed, the pressure difference between intake and exhaust is small, that is, the difference between pressure (resultant force F1) and thrust (resultant force of F2 + F3) is small. This difference is the clamping force that presses the vane 2 onto the rotor 3. As a result, the clamping force on the vane 2 is small. Thus, when, for example, after the compressor exhaust process is completed, the high-pressure medium (e.g., high-pressure liquid) in the exhaust sealed volume impacts the contact area between the vane 2 and the rotor 3, because the clamping force is small, the impact force of the high-pressure medium on the contact area between the vane 2 and the rotor 3 is greater than the clamping force that presses the vane 2 onto the rotor 3. As a result, the vane 2 will detach from the rotor 3 and then impact the rotor 3 again, thus producing abnormal noise.

[0027] Based on this, according to the first aspect of this disclosure, a cylinder block is provided, with reference to... Figures 1 to 6 As shown, the cylinder 1 is used for a rolling rotor compressor, and the cylinder 1 has a mounting cavity 110, a vane groove 120, an intake port 130, and an exhaust port 140. The mounting cavity 110 is used to accommodate the rotor 3. The vane groove 120 is located between the intake port 130 and the exhaust port 140 and is used to set the vane 2. The vane groove 120 is parallel to the center line of the mounting cavity 110. The vane groove 120 has a first reference surface 121 that is offset from the center line of the mounting cavity 110. The first reference surface 121 is located at the center position in the width direction of the vane groove 120 and is located on the side of the center line of the mounting cavity 110 near the intake port 130.

[0028] Through the above technical solution, namely the cylinder body provided in this disclosure, the sliding vane groove 120 on the cylinder body 1 is constructed to be parallel to the center line of the mounting cavity 110 and has a first reference surface 121 offset from the center line of the mounting cavity 110. This first reference surface 121 is located at the center of the width direction of the sliding vane groove 120 and is arranged on the side of the mounting cavity 110 near the intake port 130. In other words, it can be understood that by offsetting the sliding vane groove 120 on the cylinder body 1 towards the intake port 130, this disclosure increases the pressure-bearing area of ​​the sliding vane 2 on the intake port 130 side and decreases the pressure-bearing area of ​​the sliding vane 2 on the exhaust port 140 side. This reduces the thrust required to push the vane 2 away from the rotor 3, thereby increasing the clamping force of the vane 2 on the rotor 3. As a result, when the high-pressure medium (e.g., high-pressure liquid) in the exhaust closed volume (which can be understood as the closed space formed on the exhaust port 140 side) impacts the contact area between the vane 2 and the rotor 3 after the compressor exhaust process, a higher impact force is required to impact the contact area between the vane 2 and the rotor 3 to make the vane 2 separate from the rotor 3 compared to related technologies. Therefore, the cylinder 1 provided in this disclosure can reduce or even avoid the risk of the vane 2 separating from the rotor 3, thereby solving the problem of abnormal noise in the air conditioner.

[0029] It should be noted that, since this disclosure offsets the sliding vane groove 120 within the cylinder 1 toward the intake port 130, thus, reference... Figure 3 and Figure 7 As shown, compared to related technologies, the contact position between rotor 3 and vane 2 at the 0° position (where the volume of working chamber 6 is largest) has been changed, and this position is arranged closer to the exhaust port 140 side. This reduces the pressure-bearing area of ​​vane 2 on the exhaust port 140 side while increasing the pressure-bearing area of ​​vane 2 on the intake port 130 side. However, since the pressure in the compression chamber on the exhaust port 140 side (the enclosed space formed on the exhaust port 140 side) is generally greater than that on the intake port 130 side... The rated intake pressure and rated exhaust pressure, thus, reduce the pressure-bearing area of ​​the slide 2 on the exhaust port 140 side, thereby reducing the thrust that pushes the slide 2 away from the rotor 3 and increasing the clamping force of the slide 2 on the rotor 3. That is, it can be understood that, due to the reduction of the pressure-bearing area of ​​the slide 2 on the exhaust port 140 side and the increase of the pressure-bearing area of ​​the slide 2 on the intake port 130 side, the thrust (the resultant force of F2+F3) is reduced compared to the thrust experienced by the slide 2 in related technologies. Therefore, as Figure 6The increased difference between the pressure (resultant force F1) and the thrust (resultant force of F2+F3) increases the clamping force that presses the vane 2 against the rotor 3. As a result, compared to related technologies, a higher impact force is required to strike the contact area between the vane 2 and the rotor 3 to disengage the vane 2 from the rotor 3. Therefore, the cylinder 1 provided in this disclosure can reduce or even avoid the risk of the vane 2 disengaging from the rotor 3, thereby solving the problem of abnormal noise in the air conditioner.

[0030] Furthermore, it should be noted that, compared to related technologies, the contact position between the rotor 3 and the sliding vane 2 at the 0° position (where the volume of the working chamber 6 is at its maximum) has been changed, and this position is arranged closer to the exhaust port 140. Therefore, referring to... Figure 4 As shown, in, for example, rotor 3 along counterclockwise ( Figure 4 As the rotor 3 moves to a position (in the direction of the middle arrow) after the compressor exhaust process has ended, and continues to rotate towards the 0° position from that position, the pressure-bearing area of ​​the sliding vane 2 on the exhaust port 140 side gradually increases. Since the pressure-bearing area of ​​the rotor 3 on the exhaust port 140 side is the largest at the 0° position, compared to related technologies, the pressure-bearing area of ​​the sliding vane 2 on the exhaust port 140 side is also reduced during the rotation of the rotor 3 from the compressor exhaust process towards the 0° position. This reduces or even eliminates the risk of the sliding vane 2 detaching from the rotor 3, thereby solving the problem of abnormal noise in the air conditioner.

[0031] Furthermore, because this disclosure shifts the vane groove 120 on the cylinder 1 toward the intake port 130, the pressure-bearing area of ​​the vane 2 on the intake port 130 side increases, while the pressure-bearing area of ​​the vane 2 on the exhaust port 140 side decreases. This also allows for better pressure distribution after, for example, the compressor exhaust process (e.g., after the compressor exhaust process is completed). Figure 4 The position of rotor 3 shown reduces the volume occupied by vane 2 in the compression chamber (the enclosed space formed on the side of exhaust port 140), which helps to reduce the clearance volume of, for example, a rolling rotor compressor and improve the volumetric efficiency of the rolling rotor compressor.

[0032] The exhaust sealing volume mentioned above is typically less than or equal to the clearance volume. The clearance volume can be understood as the volume of volume available when rotor 3 rotates to the position described above. Figure 4After reaching the position shown, the compressor exhaust process ends. At this time, the volume of the closed space formed between the rotor 3, the vane 2, and the inner wall of the cylinder 1 is the clearance volume. As the rotor 3 continues to rotate towards the 0° position after the compressor exhaust process ends, the volume of the closed space formed between the rotor 3, the vane 2, and the inner wall of the cylinder 1 can be understood as the exhaust closed volume mentioned above.

[0033] For example, such as Figures 3 to 5 As shown, the slide groove 120 may have opposing first sidewalls 122 and second sidewalls 123. The first sidewall 122 is located on the side of the second sidewall 123 closer to the intake port 130. The first reference surface 121 is parallel to the first sidewall 122 and the second sidewall 123, and is located at the center between the first sidewall 122 and the second sidewall 123. The centerline of the mounting cavity 110 is located between the first reference surface 121 and the second sidewall 123. That is, it can be understood that, for example, the second reference surface 121 passes through the centerline of the mounting cavity 110 and is parallel to the first reference surface 121. The reference surface 4 can be located between the first reference surface 121 and the second side wall 123. In this way, the arrangement of the sliding vane groove 120 can make the sliding vane groove 120 on the cylinder 1 offset towards the intake port 130, so as to reduce the pressure area of ​​the sliding vane 2 on the exhaust port 140 side in the sliding vane groove 120. This can reduce the thrust that pushes the sliding vane 2 away from the rotor 3, thereby increasing the clamping force of the sliding vane 2 on the rotor 3, reducing or even avoiding the risk of the sliding vane 2 separating from the rotor 3, and thus solving the problem of abnormal noise in the air conditioner.

[0034] Additionally, in some implementations, references Figures 1 to 5 As shown, the cylinder body 1 may have a shaft hole 150 through which the rotating shaft 5 connected to the rotor 3 passes. The center line of the shaft hole 150 coincides with the center line of the mounting cavity 110, so as to offset the sliding vane groove 120 toward the intake port 130. In this way, during the process of the rotating shaft 5 rotating eccentrically around the center line and driving the rotor 3 to always be in contact with the inner wall of the cylinder body 1, the risk of the sliding vane 2 disengaging from the rotor 3 can be reduced or even avoided, thereby solving the problem of abnormal noise in the air conditioner.

[0035] In this disclosure, the specific structure of the rotating shaft 5, the rotor 3 and the end cover 8 is not specifically limited. The purpose is to enable the rotor 3 to always be in contact with the inner wall of the cylinder 1 through the rotating shaft 5, thereby realizing the working process of the rolling rotor compressor, such as intake, compression and exhaust. Those skilled in the art can design it adaptively according to actual application needs.

[0036] According to a second aspect of this disclosure, a cylinder assembly is provided, comprising a rotor 3, a vane 2, and a cylinder body 1 as described in the first aspect, thereby reducing or even eliminating the risk of the vane 2 disengaging from the rotor 3, and thus solving the problem of abnormal noise in the air conditioner. Furthermore, this cylinder assembly also possesses all the beneficial effects of the cylinder body 1 described in the first aspect, which will not be elaborated further herein.

[0037] In some implementations, reference Figure 3 and Figure 4 As shown, the slide 2 may have an end face 210 that contacts the rotor 3. This end face 210 is asymmetrically arranged about the first reference surface 121. In this way, by constructing the slide 2 as an asymmetrical structure, the pressure-bearing area of ​​the slide 2 on the intake port 130 side is made larger than the pressure-bearing area of ​​the slide 2 on the exhaust port 140 side. This reduces the thrust that pushes the slide 2 away from the rotor 3, thereby increasing the clamping force of the slide 2 on the rotor 3 and reducing or even avoiding the risk of the slide 2 separating from the rotor 3.

[0038] In this invention, considering that in related technologies, the vane groove 120 and the vane 2 are usually symmetrical structures, after the vane groove 120 in the cylinder 1 is offset toward the intake port 130, when the rotor 3 rotates to the 0° position (the working chamber 6 has the largest volume), the contact point between the rotor 3 and the vane 2 will shift, and the tangent 7 of the contact point will also change. Therefore, the first reference surface 121 can be redesigned so that the vane 2 is asymmetrically arranged about the first reference surface 121, so as to ensure that the vane 2 is tightly attached to the outer periphery of the rotor 3 during the rotation of the rotor 3, which helps to improve the operational reliability of the cylinder assembly.

[0039] For example, exemplarily, in some implementations, reference is made to Figures 3 to 6 As shown, a working cavity 6 is formed between the rotor 3 and the inner wall of the mounting cavity 110. The vane 2 may have an end face 210 that contacts the rotor 3. The end face 210 includes a first guide surface 211 and a second guide surface 212. The first guide surface 211 is close to the intake port 130, and the second guide surface 212 is close to the exhaust port 140. The connection between the first guide surface 211 and the second guide surface 212 contacts the rotor 3 when the volume of the working cavity 6 is at its maximum. In this way, by making the connection between the first guide surface 211 and the second guide surface 212 of the vane 2 contact the rotor 3 when the rotor 3 rotates to the 0° position (when the volume of the working cavity 6 is at its maximum), it is beneficial to ensure that the vane 2 is tightly attached to the outer periphery of the rotor 3 during the rotation of the rotor 3, thereby improving the reliability of operation and ensuring that the working cavity 6 has a large maximum suction volume, thus improving the volumetric efficiency of, for example, a rolling rotor compressor.

[0040] Among them, such as Figures 3 to 6As shown, the first guide surface 211 and the second guide surface 212 can be configured such that the tangent surface 7 at the connection is perpendicular to the first reference surface 121, which helps to improve the operational reliability of the cylinder assembly.

[0041] Additionally, in some implementations, references Figure 3 and Figure 6 As shown, the area of ​​the first guide surface 211 can be larger than the area of ​​the second guide surface 212, so that the pressure-bearing area of ​​the slide plate 2 on the intake port 130 side is greater than the pressure-bearing area of ​​the slide plate 2 on the exhaust port 140 side, thereby reducing the thrust that pushes the slide plate 2 away from the rotor 3 and increasing the clamping force of the slide plate 2 on the rotor 3. Thus, when the high-pressure medium (e.g., high-pressure liquid) in the exhaust closed volume (which can be understood as the closed space formed on the exhaust port 140 side) impacts the contact part between the slide plate 2 and the rotor 3 after the compressor exhaust process, a higher impact force is required to impact the contact part between the slide plate 2 and the rotor 3 compared to related technologies, so that the slide plate 2 can be separated from the rotor 3, reducing or even avoiding the risk of the slide plate 2 separating from the rotor 3.

[0042] Furthermore, considering the need to improve the operational reliability of the cylinder assembly, in some embodiments, the first guide surface 211 and / or the second guide surface 212 can be curved surfaces, for example, such as... Figure 3 and Figure 6 As shown, the first guide surface 211 and the second guide surface 212 can both be constructed as arc surfaces, so as to ensure that the arc surface of the slide plate 2 is always closely attached to the outer periphery of the rotor 3 during the rotation of the rotor 3, which helps to improve the operational reliability of the cylinder assembly.

[0043] Among them, such as Figure 3 and Figure 6 As shown, the radius R of the arc surface of the first guide surface 211 can be greater than the radius r of the arc surface of the second guide surface 212. For example, the radius R of the arc surface of the first guide surface 211 can be, for example, 3mm-8mm, or for example, 5mm. In addition, the radius r of the arc surface of the second guide surface 212 can be, for example, 2.5mm-5mm, or for example, 3.2mm. This is to ensure that the bearing area of ​​the slide plate 2 on the intake port 130 side is greater than the bearing area of ​​the slide plate 2 on the exhaust port 140 side, so as to reduce the thrust that pushes the slide plate 2 away from the rotor 3, thereby increasing the clamping force of the slide plate 2 on the rotor 3, and reducing or even avoiding the risk of the slide plate 2 separating from the rotor 3.

[0044] It should be noted that the specific embodiments of the arc radius R of the first guide surface 211 and the arc radius r of the second guide surface 212 described above are exemplary. Those skilled in the art can adaptively design the arc radius R of the first guide surface 211 and the arc radius r of the second guide surface 212 according to actual application requirements. This disclosure is not limited thereto. Of course, in some other embodiments not shown, the first guide surface 211 and the second guide surface 212 may also be, for example, inclined surfaces.

[0045] Additionally, in some implementations, references Figure 3 and Figure 6 As shown, the slider 2 may have opposing third sidewalls 220 and fourth sidewalls 230. The third sidewall 220 is near the intake port 130, and the fourth sidewall 230 is near the exhaust port 140. The distance 'a' between the connection point of the first guide surface 211 and the second guide surface 212 and the third sidewall 220 is greater than the distance 'b' between the connection point and the fourth sidewall 230. For example, the distance 'a' between the connection point of the first guide surface 211 and the second guide surface 212 and the third sidewall 220 may be, for example, 1.6 mm, and the distance 'b' between the connection point of the first guide surface 211 and the second guide surface 212 and the fourth sidewall 230 may be, for example, 1.4 mm, so as to facilitate the... After the vane groove 120 in the cylinder 1 is offset toward the intake port 130, it ensures that the connection between the first guide surface 211 and the second guide surface 212 contacts the rotor 3 when the volume of the working chamber 6 is at its maximum. This helps to improve the operational reliability of the cylinder assembly. At the same time, it also enables the contact position between the rotor 3 and the vane 2 at the 0° position to be arranged close to the exhaust port 140 side, reducing the pressure area of ​​the vane 2 on the exhaust port 140 side. This reduces the thrust that pushes the vane 2 away from the rotor 3, thereby increasing the clamping force of the vane 2 on the rotor 3, reducing or even avoiding the risk of the vane 2 separating from the rotor 3, and thus solving the problem of abnormal noise in the air conditioner.

[0046] According to a third aspect of this disclosure, a rolling rotor compressor is provided, which includes the cylinder assembly provided in the second aspect above. Furthermore, the rolling rotor compressor has all the beneficial effects of the cylinder assembly provided in the second aspect above, which will not be elaborated further herein.

[0047] According to a fourth aspect of this disclosure, an outdoor unit is provided, which includes the rolling rotor compressor provided in the third aspect above. Furthermore, the outdoor unit possesses all the beneficial effects of the rolling rotor compressor provided in the third aspect above, which will not be elaborated further herein.

[0048] According to a fifth aspect of this disclosure, an air conditioner is provided, which includes the outdoor unit provided in the fourth aspect above. Furthermore, this air conditioner possesses all the beneficial effects of the outdoor unit provided in the fourth aspect above, which will not be elaborated further herein.

[0049] The preferred embodiments of this disclosure have been described in detail above with reference to the accompanying drawings. However, this disclosure is not limited to the specific details of the above embodiments. Within the scope of the technical concept of this disclosure, various simple modifications can be made to the technical solutions of this disclosure, and these simple modifications all fall within the protection scope of this disclosure.

[0050] It should also be noted that the various specific technical features described in the above embodiments can be combined in any suitable manner without contradiction. To avoid unnecessary repetition, this disclosure will not describe the various possible combinations separately.

[0051] Furthermore, various different embodiments of this disclosure can be combined in any way, as long as they do not violate the spirit of this disclosure, they should also be regarded as the content disclosed in this disclosure.

Claims

1. A cylinder for a rolling piston compressor, characterized in that, The cylinder has a mounting cavity, a vane groove, an intake port, and an exhaust port. The mounting cavity is used to accommodate a rotor. The vane groove is located between the intake port and the exhaust port and is used to set vanes. The vane groove is parallel to the centerline of the mounting cavity. The vane groove has a first reference surface that is offset from the centerline of the mounting cavity. The first reference surface is located at the center of the width direction of the vane groove and is located on the side of the centerline of the mounting cavity closer to the intake port.

2. The cylinder of claim 1, wherein The slide groove has a first sidewall and a second sidewall opposite to each other. The first sidewall is located on the side of the second sidewall closer to the air inlet. The first reference surface is parallel to the first sidewall and the second sidewall and is located at the center between the first sidewall and the second sidewall. The centerline of the mounting cavity is located between the first reference surface and the second sidewall.

3. Cylinder according to claim 1 or 2, characterized in that The cylinder has a shaft hole through which the shaft connected to the rotor passes, and the center line of the shaft hole coincides with the center line of the mounting cavity.

4. A cylinder assembly characterized by, It includes a rotor, vanes, and a cylinder block as described in any one of claims 1-3.

5. The cylinder assembly of claim 4, wherein, The slide has an end face that contacts the rotor, and the end face is arranged asymmetrically about the first reference plane.

6. The cylinder assembly of claim 4, wherein, A working cavity is formed between the rotor and the inner wall of the mounting cavity. The slide has an end face that contacts the rotor. The end face includes a first guide surface and a second guide surface. The first guide surface is close to the intake port, and the second guide surface is close to the exhaust port. The connection between the first guide surface and the second guide surface contacts the rotor when the volume of the working cavity is at its maximum.

7. The cylinder assembly of claim 6, wherein, The first guide surface and the second guide surface are configured such that the cut surface tangent to the connection is perpendicular to the first reference surface.

8. The cylinder assembly of claim 6, wherein, The area of ​​the first guide surface is greater than the area of ​​the second guide surface.

9. The cylinder assembly of any of claims 6-8, wherein, The first guide surface and / or the second guide surface are curved surfaces.

10. The cylinder assembly of claim 9, wherein, The radius of the arc surface of the first guide surface is greater than the radius of the arc surface of the second guide surface.

11. The cylinder assembly of claim 10, wherein, The radius of the arc surface of the first guide surface is 3mm-8mm; and / or, The radius of the arc surface of the second guide surface is 2.5mm-5mm.

12. The cylinder assembly of claim 6, wherein, The slide has a third sidewall and a fourth sidewall, the third sidewall being close to the intake port and the fourth sidewall being close to the exhaust port. The distance between the connection point of the first guide surface and the second guide surface and the third sidewall is greater than the distance between the connection point and the fourth sidewall.

13. A rolling piston compressor, characterized by Includes the cylinder assembly as described in any one of claims 4-12.

14. An outdoor unit characterized by comprising: Including the rolling rotor compressor as described in claim 13.

15. An air conditioner characterized by comprising: Includes the outdoor unit as described in claim 14.

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