Enthalpy-increasing rotor type compressor and air conditioner

Abstract

The enthalpy-increasing rotor type compressor comprises a machine shell with a containing space, a pump body assembly assembled in the containing space and an enthalpy-increasing assembly located on the outer side of the machine shell, the pump body assembly is provided with an enthalpy-increasing hole, a through hole corresponding to the enthalpy-increasing hole in position is formed in the machine shell, and the enthalpy-increasing assembly is located on the outer side of the machine shell. The enthalpy increasing assembly comprises an enthalpy increasing injection needle, the enthalpy increasing injection needle is inserted into the enthalpy increasing hole through the through hole, an annular gap is formed between the enthalpy increasing injection needle and the enthalpy increasing hole, and a sealing ring is arranged in the annular gap so that the annular gap can be sealed. The mechanical efficiency of the pump body is improved, the energy efficiency of the compressor is improved, the abnormal conditions that the pump body assembly is stuck and the compressor cannot operate are prevented, and the one-time passing rate and the long-term reliability of the pump body assembly are improved.

Description

Technical Field

[0001] This invention belongs to the field of air conditioning design technology, specifically relating to an enthalpy-increasing rotor compressor and an air conditioner. Background Technology

[0002] In general, rotary compressors use non-tightly fitted copper sealing rings to seal the cylinder suction port and the distributor. However, in enthalpy-increasing rotary compressors, the enthalpy-increasing distributor is usually smaller and uses an injection needle assembly structure for sealing. The injection needle is usually pressed into the pump body partition or upper and lower flanges after the pump body assembly is centered and assembled. This sequential assembly relationship leads to displacement of the compressor pump body assembly gap (mainly radial gap displacement) during production, unstable or poor centering gap, abnormal noise from the compressor, and frequent electromagnetic noise (due to the change in mechanical structure caused by gap displacement, the natural frequency of the mechanical structure is close to the operating frequency of the motor, resulting in electromagnetic noise). This reduces the mechanical efficiency of the pump body, affects the energy efficiency of the compressor (increased power consumption), and in severe cases, the pump body assembly may seize up or the compressor may fail to operate. Summary of the Invention

[0003] Therefore, the present invention provides an enthalpy-increasing rotor compressor and an air conditioner that can overcome the shortcomings of related technologies, such as interference fit between the enthalpy-increasing injection needle assembly and the partition or upper and lower flanges. Because this assembly process is after the centering assembly process of the pump body assembly, it causes displacement of the pump body assembly gap, unstable or poor centering gap, abnormal noise of the compressor, and frequent electromagnetic noise, which reduces the mechanical efficiency of the pump body, affects the energy efficiency of the compressor, and in severe cases, the pump body assembly may jam or the compressor may fail to operate.

[0004] To address the aforementioned problems, this invention provides an enthalpy-increasing rotary compressor, comprising a housing with a accommodating space, a pump assembly assembled within the accommodating space, and an enthalpy-increasing component located outside the housing. The pump assembly has an enthalpy-increasing orifice, and the housing has a through hole corresponding to the position of the enthalpy-increasing orifice. The enthalpy-increasing component includes an enthalpy-increasing injection needle, which is inserted into the enthalpy-increasing orifice via the through hole. An annular gap exists between the enthalpy-increasing injection needle and the enthalpy-increasing orifice, and a sealing ring is provided within the annular gap to seal it.

[0005] In some embodiments, the radial width of the annular gap is 0.6 mm to 1.15 mm.

[0006] In some embodiments, the pump assembly includes a baffle, and the enthalpy-increasing orifice is formed on the outer circumferential wall of the baffle and extends radially along the pump assembly.

[0007] In some embodiments, a receiving annular groove for accommodating the sealing ring is formed on the outer circumferential wall surface of the enthalpy-increasing injection needle, and / or, a receiving annular groove for accommodating the sealing ring is formed on the inner circumferential wall surface of the enthalpy-increasing orifice.

[0008] In some embodiments, the enthalpy-increasing injection needle is sealed and welded to the housing at the region of the through hole; and / or, a plurality of accommodating annular grooves are provided at axial intervals along the enthalpy-increasing injection needle.

[0009] In some embodiments, the enthalpy-increasing injection needle includes a first tube segment and a second tube segment. The first end of the first tube segment and the first end of the second tube segment are sealed together internally and externally. The second end of the first tube segment is connected to the enthalpy enhancer of the enthalpy-increasing assembly. The second end of the second tube segment is inserted into the enthalpy-increasing hole, and the sealing ring is fitted onto the second tube segment. The first tube segment is welded to the housing, and the fitting area between the first tube segment and the second tube segment is provided with a heat insulation layer.

[0010] In some implementations, the first pipe section, the second pipe section, and the housing are made of the same material.

[0011] In some embodiments, the width of the receiving annular groove is 1.1 to 1.5 times the maximum diameter of the sealing ring in the assembled state; and / or, the wall roughness of the receiving annular groove is Ra = 3.2 μm to 6.3 μm.

[0012] In some embodiments, the sealing ring is an O-ring, the compression ratio of the O-ring is W, 10%≤W≤15%; and / or, the stretch of the sealing ring is 5%~30%.

[0013] In some embodiments, the width of the O-ring after deformation when the sealing ring is in the assembled state is B0, and the cross-sectional diameter of the O-ring when the sealing ring is in the free state is d0, 1.05≤B0 / d0≤1.09; and / or, B0=[1 / (1-W)-0.6W]d0.

[0014] In some embodiments, when the O-ring is in the assembled state, the width of the contact surface between the O-ring and the outer circumferential wall of the enthalpy-increasing injection needle is b, where b = (4W) 2 +0.34W+0.31)d0, wherein the cross-sectional diameter of the O-ring is d0 when the sealing ring is in a free state, and / or the groove depth S of the receiving annular groove is (1-W)d0.

[0015] The present invention also provides an air conditioner, including the above-described enthalpy-increasing rotary compressor.

[0016] The enthalpy-increasing rotary compressor and air conditioner provided by this invention have the following beneficial effects: This application improves upon the traditional interference fit between the enthalpy-increasing injection needle and the enthalpy-increasing orifice by using a clearance fit and adding a corresponding sealing ring to achieve an annular gap seal between them. This eliminates the problem in the prior art where the assembly pressure applied during the interference fit assembly of the enthalpy-increasing injection needle alters the gaps between the components within the pump body assembly, causing gap displacement. This, in turn, leads to unstable or poor centering gaps in the pump body assembly, resulting in abnormal noises or even electromagnetic noises from the compressor. This improves the mechanical efficiency of the pump body, enhances the energy efficiency of the compressor, prevents abnormal situations such as pump body assembly jamming and compressor malfunction, and increases the first-pass yield and long-term reliability of the pump body assembly. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the accompanying drawings used in the description of the embodiments or related technologies will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the enthalpy-increasing rotary compressor of the present invention in an embodiment of the assembled state of the enthalpy-increasing injection needle and the partition plate; Figure 2 yes Figure 1 A schematic diagram of the axial projection of the partition in the middle; Figure 3 yes Figure 2 Cross-sectional view of AA in the middle; Figure 4 This is a schematic diagram of the enthalpy-increasing injection needle in another embodiment of the enthalpy-increasing rotor compressor of the present invention.

[0019] The attached figures are labeled as follows: 1. Enthalpy-increasing injection needle; 11. First pipe section; 12. Second pipe section; 2. Sealing ring; 21. Receiving annular groove; 3. Partition plate; 100. Enthalpy-increasing orifice. Detailed Implementation

[0020] 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 some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0021] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0022] 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° or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0023] 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 should not be construed as limiting the scope of protection of this invention.

[0024] See also Figures 1 to 4As shown in the figure, according to an embodiment of the present invention, an enthalpy-increasing rotary compressor is provided, including a housing (not shown or labeled in the figure) having a accommodating space, a pump assembly (not shown or labeled in the figure) assembled in the accommodating space, and an enthalpy-increasing assembly (not shown or labeled in the figure) located outside the housing. The pump assembly has an enthalpy-increasing orifice 100, the outlet of which is controllably connected to a corresponding compression chamber (not shown in the figure). The housing has a connection to the enthalpy-increasing orifice 100. The through hole corresponding to position 00 (not shown in the figure) generally has a diameter slightly larger than the inlet diameter of the enthalpy-increasing orifice 100. The enthalpy-increasing assembly includes an enthalpy-increasing injection needle 1, which is inserted into the enthalpy-increasing orifice 100 through the through hole. There is an annular gap (not indicated in the figure) between the enthalpy-increasing injection needle 1 and the enthalpy-increasing orifice 100, that is, there is a clearance fit between the enthalpy-increasing injection needle 1 and the enthalpy-increasing orifice 100. A sealing ring 2 is provided in the annular gap to seal the annular gap. The aforementioned sealing ring 2 is specifically an elastic sealing ring, which can generally be made of synthetic rubber materials such as acrylic rubber, nitrile rubber, neoprene rubber, or fluororubber.

[0025] In this technical solution, the traditional interference fit between the enthalpy-increasing injection needle and the enthalpy-increasing orifice is improved to a clearance fit and a corresponding sealing ring 2 is added to achieve a sealing of the annular gap between the two. This can prevent the assembly pressure applied by the enthalpy-increasing injection needle during the interference fit assembly process in the prior art from changing the gap between the components in the pump body assembly, i.e., causing gap displacement, which leads to unstable or poor centering gap of the pump body assembly, abnormal noise or even electromagnetic noise from the compressor, etc. This improves the mechanical efficiency of the pump body, improves the energy efficiency of the compressor, prevents abnormal situations such as pump body assembly jamming and compressor failure, and improves the first pass rate and long-term reliability of the pump body assembly.

[0026] In some embodiments, the radial width of the annular gap is 0.6 mm to 1.15 mm, and the aforementioned radial width is also the single-sided gap width of the annular gap.

[0027] In this technical solution, limiting the width of the single-sided gap of the annular gap to between 0.6mm and 1.15mm can prevent the gap from being too large, which would reduce the sealing effect, or too small, which would place excessively high requirements on the machining accuracy of the outer circumferential wall of the enthalpy-increasing injection needle 1 and the inner circumferential wall of the enthalpy-increasing hole 100.

[0028] It is understood that, for the pump body assembly of a rotary compressor, the pump body assembly is provided with a cylinder and an upper flange and a lower flange that seal the axial ends of the cylinder. The aforementioned upper flange and lower flange also serve as rotating support components for the crankshaft. In some embodiments, the enthalpy-increasing orifice 100 can be formed on the upper flange (upper bearing) and the lower flange (lower bearing). In a preferred embodiment, for a twin-cylinder rotary compressor, the corresponding pump body assembly includes a partition 3, which is located between two upper and lower cylinders. The enthalpy-increasing orifice 100 is formed on the outer circumferential wall of the partition 3 and extends radially along the pump body assembly. Specifically, selective air replenishment to the upper cylinder and / or the lower cylinder can be achieved by setting the air replenishment channel in the enthalpy-increasing orifice 100.

[0029] In some embodiments, a receiving annular groove 21 for accommodating the sealing ring 2 is formed on the outer circumferential wall surface of the enthalpy-increasing injection needle 1, and / or a receiving annular groove 21 for accommodating the sealing ring 2 is formed on the inner circumferential wall surface of the enthalpy-increasing orifice 100. That is, the aforementioned receiving annular groove 21 can be separately disposed on the outer circumferential wall surface of the enthalpy-increasing injection needle 1 or on the inner circumferential wall surface of the enthalpy-increasing orifice 100, or it can be constructed on both simultaneously. As a preferred embodiment, the aforementioned receiving annular groove 21 is formed on the inner circumferential wall surface of the enthalpy-increasing orifice 100, which can prevent the outer diameter or wall thickness of the injection needle 1 from being too large if the receiving annular groove 21 is formed on the outer circumferential wall of the enthalpy-increasing injection needle 1.

[0030] In this technical solution, by setting a corresponding receiving annular groove 21 on the inner wall of the enthalpy-increasing injection needle 1 and / or the enthalpy-increasing hole 100, the sealing ring 2 can be accommodated, thereby ensuring that the relative position of the sealing ring 2 is reliable and stable, and thus ensuring the sealing effect.

[0031] In some embodiments, the enthalpy-increasing injection needle 1 is sealed and welded to the housing at the region of the through hole, so as to ensure that the position of the enthalpy-increasing injection needle 1 is reliable and stable, while achieving a reliable seal for the mating area between the enthalpy-increasing injection needle 1 and the through hole of the housing.

[0032] In some embodiments, the receiving annular grooves 21 are provided in multiple spaces along the axial direction of the enthalpy-increasing injection needle 1 to further improve the connection and sealing between the enthalpy-increasing injection needle 1 and the enthalpy-increasing orifice 100.

[0033] In some embodiments, the aforementioned enthalpy-increasing injection needle 1 can be implemented as an integrated structure, especially when the sealing ring 2 is far from the welding position between the enthalpy-increasing injection needle 1 and the housing. Considering that the welding heat will not be excessively conducted to the sealing ring 2 and cause burns or other damage to the sealing ring 2, an integrated structure can be considered. However, when the distance between the sealing ring 2 and the welding position between the enthalpy-increasing injection needle 1 and the housing is small, the following solution is preferred: the enthalpy-increasing injection needle 1 is divided into an assembled first tube segment 11 and a second tube segment 12, with the first end of the first tube segment 11 and the second tube segment 12 connected together. The first end of the first pipe section 11 is sealed with an inner and outer sleeve. The second end of the first pipe section 11 is connected to the enthalpy enhancer (not shown in the figure, not labeled) of the enthalpy enhancer assembly. The second end of the second pipe section 12 is inserted into the enthalpy enhancer hole 100, and the sealing ring 2 is fitted onto the second pipe section 12. The first pipe section 11 is welded to the housing. The fitting area between the first pipe section 11 and the second pipe section 12 is provided with a heat insulation layer. The aforementioned heat insulation layer can be made of a non-metallic material with a low thermal conductivity (e.g., heat insulation felt sandwiched between the first pipe section 11 and the second pipe section 12).

[0034] In this technical solution, the enthalpy-increasing injection needle 1 is formed by assembling a first tube segment 11 and a second tube segment 12 and setting an insulation layer between them. This can minimize the amount of welding heat transferred to the second tube segment 12 when welding the first tube segment 11 to the housing, thereby reducing the risk of damage such as burning of the aforementioned sealing ring 2 by the high temperature of welding, and reducing the difficulty of selecting the sealing ring 2.

[0035] In some embodiments, the first pipe section 11, the second pipe section 12, and the housing are made of the same material, such as stainless steel, which can reduce manufacturing costs. More importantly, the fact that the first pipe section 11 and the housing are made of the same material can also reduce welding difficulty, ensure welding quality, and thus ensure sealing effect.

[0036] In some embodiments, the sealing ring 2 is an O-ring, and the compression ratio of the O-ring is W, where 10% ≤ W ≤ 15%. When the compression ratio of the sealing ring 2 is lower than the aforementioned range, the O-ring does not seal properly, increasing the risk of leakage and thus failing to achieve a good sealing effect. When the compression ratio is higher than the aforementioned range, i.e., when the compression ratio is too large, the friction increases, shortening the service life of the O-ring.

[0037] Specifically, the O-ring compression ratio W is usually expressed by the following formula: W=(d0-h) / do, In the formula, d0 is the cross-sectional diameter (mm) of the O-ring in its free state. h is the distance between the bottom wall of the O-ring and the surface being sealed, i.e., the cross-sectional height (mm) of the O-ring after compression.

[0038] When selecting the compression ratio of an O-ring, the following three aspects should be considered: a. Sufficient sealing contact area; b. Minimal friction; c. Minimize permanent deformation.

[0039] It is not difficult to see from the above factors that there are contradictions among them. A high compression ratio can obtain a high contact pressure, but an excessively high compression ratio will undoubtedly increase sliding friction and permanent deformation, while an excessively low compression ratio may cause leakage due to the coaxiality error of the receiving ring groove 21 and the non-compliance of the O-ring seal error. Therefore, when selecting the compression ratio of the O-ring seal, various factors must be weighed. Generally, the compression ratio of static seals is greater than that of dynamic seals, but its extreme value should be less than 30% (related to the rubber material), otherwise the compressive stress will be significantly relaxed, resulting in excessive permanent deformation, which is particularly serious in high-temperature conditions.

[0040] The selection of the O-ring sealing compression ratio W should consider the usage conditions, whether it is a static or dynamic seal. Static seals can be further divided into radial seals and axial seals. The leakage gap of a radial seal (or cylindrical static seal) is the radial gap, while the leakage gap of an axial seal (or planar static seal) is the axial gap. Axial seals are further divided into two cases: internal pressure and external pressure, depending on whether the pressure medium acts on the inner or outer diameter of the O-ring. Internal pressure increases the tension, while external pressure decreases the initial tension of the O-ring. For the above-mentioned different types of static seals, the direction of the force exerted by the sealing medium on the O-ring is different, so the pre-pressure design is also different. In this application, the sealing ring 2 objectively forms a cylindrical static seal device, with W = 10%~15%.

[0041] In some embodiments, when the sealing ring 2 is fitted onto the outer circumferential wall of the enthalpy-increasing injection needle 1, the stretch of the sealing ring 2 should be 5% to 30%.

[0042] In this technical solution, the stretching amount of the sealing ring 2 is reasonably limited to prevent the O-ring from being difficult to install due to excessive stretching, and to prevent the compression rate from decreasing due to changes in the cross-sectional diameter of the sealing ring 2, which could lead to leakage. It also prevents the O-ring from being overstretched during operation, which could accelerate aging and cause leakage.

[0043] The dimensions of the receiving ring groove 21 depend on the dimensions of the O-ring. The dimensions of the receiving ring groove 21 can be calculated by volume. In a specific embodiment, the receiving ring groove 21 is a rectangular groove. The dimensions of the rectangular groove should be about 15% larger than the volume of the O-ring. This is because: a. After the O-ring is installed in the receiving ring groove 21, it is subjected to 3% to 30% compression. Since the rubber material itself is incompressible, there should be space to accommodate the deformed part of the O-ring; b. For O-rings in oil, in addition to the possible expansion of the rubber material due to immersion in the oil, there may also be expansion of the rubber material as the working temperature of the liquid increases. Therefore, the receiving ring groove 21 must have a certain margin; c. In motion, it can accommodate the slight rolling phenomenon that the O-ring may produce. Therefore, it is necessary to leave an appropriate gap between the assembled O-ring and the groove wall of the receiving ring groove 21. However, this gap should not be too large, otherwise it will become a harmful "playback" under alternating pressure, increasing the wear of the O-ring. The groove width of the receiving ring groove 21 should not be too small. If the cross-section of the O-ring fills the cross-section of the groove, the frictional resistance during movement will be particularly large, the O-ring will not be able to roll, and it will cause serious wear. The groove width of the receiving ring groove 21 should not be too large either, because when the groove is too large, the O-ring will have a large range of movement and will be prone to wear. Especially in static sealing, if the working pressure is pulsating, the static seal will not be static. It will move in the unsuitable wide groove at the same pulsating frequency, resulting in abnormal wear and causing the O-ring to fail quickly. The cross-sectional area of ​​the O-ring should be at least 85% of the cross-sectional area of ​​the rectangular groove, and the groove width must be greater than the maximum diameter of the O-ring after compression deformation. Specifically, the groove width should be 1.1 to 1.5 times the maximum diameter of the O-ring after compression deformation in the assembled state. When the groove width is greater than 1.5 times the cross-sectional diameter of the O-ring, the O-ring will not seal properly, increasing the risk of leakage, i.e., a good sealing effect cannot be achieved. When the groove width is less than 1.1 times the cross-sectional diameter of the O-ring, the O-ring will be excessively compressed, increasing friction and shortening the service life of the O-ring. The aforementioned assembled state refers to the state in which the sealing ring 2 is clamped between the enthalpy injection needle 1 and the enthalpy orifice 100 and compressed, which corresponds to the unassembled, free state of the sealing ring 2.

[0044] The surface roughness of the receiving annular groove 21 directly affects the sealing performance of the O-ring and the manufacturability of the receiving annular groove 21. The sealing ring 2 in this application is a static seal. In order to ensure that the O-ring for static sealing does not move during operation, the groove wall roughness (surface roughness) Ra of the receiving annular groove 21 can be 3.2μm ~ 6.3μm.

[0045] After the O-ring is inserted into the receiving annular groove 21, its cross-section undergoes compressive deformation. The width of the deformed O-ring and its contact width with the shaft are related to the sealing performance and service life of the O-ring. If the value is too small, the sealing performance will be affected; if it is too large, friction will be increased, generating frictional heat and affecting the life of the O-ring. To make the design more reasonable, in some embodiments, the width of the O-ring after deformation when the sealing ring 2 is in the assembled state is B0, and the cross-sectional diameter of the O-ring when the sealing ring 2 is in the free state is d0, where 1.05 ≤ B0 / d0 ≤ 1.09. In a specific embodiment, the unit of the aforementioned B0 is mm.

[0046] In some embodiments, B0 = [1 / (1-W)-0.6W]d0, where the width of the contact surface between the O-ring and the outer circumferential wall of the enthalpy-increasing injection needle 1 in the assembled state of the sealing ring 2 is b, and b = (4W) / (1-W)-0.6W)d0. 2 +0.34W+0.31)d0, where the cross-sectional diameter of the O-ring seal 2 in its free state is d0. In a specific embodiment, the unit of the aforementioned b is mm.

[0047] The ratio of the groove depth S of the receiving ring groove 21 to the cross-sectional diameter d0 of the O-ring determines the compression ratio of the O-ring. To obtain a suitable compression ratio, the groove depth of the receiving ring groove 21 should satisfy: S = (1-W) d0 to ensure the deformation of the O-ring required for sealing.

[0048] The outer edge of the receiving annular groove 21 is designed with rounded corners to prevent the O-ring from being scratched during assembly. The radius of this rounded corner is r = 0.1~0.2mm. This avoids the formation of sharp edges, prevents the O-ring from being squeezed out, and ensures stable placement of the O-ring. The bottom of the receiving annular groove 21 also has rounded corners, which are designed to avoid stress concentration. The radius of the rounded corner is R, where R = d0 / 2. In a specific embodiment, the unit of R is mm.

[0049] It should be noted that the sealing reliability of the O-ring 2 in the annular gap mainly depends on the compression of the O-ring. Under normal circumstances, this compression is very small, only a few tens of micrometers. This requires the O-ring to have very high dimensional tolerances. Therefore, the O-ring needs to be processed using high-precision molds, and the shrinkage rate of the O-ring material, which is the basis for the design, must be accurately determined. Generally, the shrinkage rate of the O-ring can only be obtained through actual measurement. In this invention, the cross-sectional diameter of the O-ring is less than 8mm, and the cross-sectional shrinkage rate is very small and generally not considered. Under certain formulation and process conditions, the shrinkage rate of the O-ring will decrease with increasing material hardness and increase with decreasing inner diameter.

[0050] The present invention also provides an air conditioner, including the above-described enthalpy-increasing rotary compressor.

[0051] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0052] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. An enthalpy-increasing rotary compressor, characterized in that, The device includes a housing with a accommodating space, a pump assembly assembled within the accommodating space, and an enthalpy-increasing assembly located outside the housing. The pump assembly has an enthalpy-increasing orifice (100). A through hole corresponding to the position of the enthalpy-increasing orifice (100) is formed on the housing. The enthalpy-increasing assembly includes an enthalpy-increasing injection needle (1). The enthalpy-increasing injection needle (1) is inserted into the enthalpy-increasing orifice (100) through the through hole. An annular gap exists between the enthalpy-increasing injection needle (1) and the enthalpy-increasing orifice (100). A sealing ring (2) is provided in the annular gap to seal the annular gap.

2. The enthalpy-increasing rotary compressor according to claim 1, characterized in that, The radial width of the annular gap is 0.6 mm to 1.15 mm.

3. The enthalpy-increasing rotary compressor according to claim 1 or 2, characterized in that, The pump assembly includes a partition (3), and the enthalpy-increasing orifice (100) is formed on the outer circumferential wall of the partition (3) and extends radially along the pump assembly.

4. The enthalpy-increasing rotary compressor according to claim 3, characterized in that, The outer circumferential wall of the enthalpy-increasing injection needle (1) has a receiving annular groove (21) for accommodating the sealing ring (2), and / or the inner circumferential wall of the enthalpy-increasing hole (100) has a receiving annular groove (21) for accommodating the sealing ring (2).

5. The enthalpy-increasing rotary compressor according to claim 4, characterized in that, The enthalpy-increasing injection needle (1) is sealed and welded to the housing at the region of the through hole; and / or, the receiving annular groove (21) is provided in a plurality of spaces along the axial direction of the enthalpy-increasing injection needle (1).

6. The enthalpy-increasing rotary compressor according to claim 5, characterized in that, The enthalpy-increasing injection needle (1) includes a first tube section (11) and a second tube section (12). The first end of the first tube section (11) and the first end of the second tube section (12) are sealed together. The second end of the first tube section (11) is connected to the enthalpy enhancer of the enthalpy-increasing assembly. The second end of the second tube section (12) is inserted into the enthalpy-increasing hole (100). The sealing ring (2) is fitted onto the second tube section (12). The first tube section (11) is welded to the housing. The fitting area between the first tube section (11) and the second tube section (12) is provided with a heat insulation layer.

7. The enthalpy-increasing rotary compressor according to claim 6, characterized in that, The first pipe section (11), the second pipe section (12), and the casing are made of the same material.

8. The enthalpy-increasing rotary compressor according to claim 4, characterized in that, The groove width of the accommodating annular groove (21) is 1.1 to 1.5 times the maximum diameter of the sealing ring (2) in the assembled state; and / or, the groove wall roughness Ra of the accommodating annular groove (21) is 3.2 μm to 6.3 μm.

9. The enthalpy-increasing rotary compressor according to claim 1, characterized in that, The sealing ring (2) is an O-ring, the compression rate of the O-ring is W, 10%≤W≤15%; and / or, the stretch of the sealing ring (2) is 5%~30%.

10. The enthalpy-increasing rotary compressor according to claim 9, characterized in that, When the sealing ring (2) is in the assembled state, the width of the O-ring after deformation is B0, and when the sealing ring (2) is in the free state, the cross-sectional diameter of the O-ring is d0, 1.05≤B0 / d0≤1.09; and / or, B0=[1 / (1-W)-0.6W]d0.

11. The enthalpy-increasing rotary compressor according to claim 9, characterized in that, When the sealing ring (2) is in the assembled state, the width of the contact surface between the O-ring and the outer circumferential wall of the enthalpy-increasing injection needle (1) is b, b = (4W 2 +0.34W+0.31)d0, wherein the cross-sectional diameter of the O-ring is d0 when the sealing ring (2) is in a free state, and / or the groove depth S of the accommodating annular groove (21) is S = (1-W)d0.

12. An air conditioner, characterized in that, The enthalpy-increasing rotary compressor includes any one of claims 1 to 11.

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