A sleeve structure for stator cooling of a compressor and a heat pump unit

Abstract

This invention discloses a bushing structure for stator cooling of a compressor and a heat pump unit. The bushing structure includes a bushing body fitted onto the compressor stator. The bushing structure also includes a first flow channel and a second flow channel symmetrically distributed on the bushing body, both spirally distributed on the surface of the bushing body. Compared with the prior art, this invention improves the heat dissipation uniformity of the compressor stator through the symmetrically distributed first and second flow channels on the bushing body, avoiding the problem of poor cooling in the later stages due to unilateral cooling water introduction. Furthermore, by adding turbulent fins to create turbulence, the cooling water flow is accelerated, significantly reducing the compressor stator temperature. The use of a sealing ring design prevents cooling water from entering the motor cavity, ensuring the reliability of motor operation.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a bushing structure for stator cooling of a compressor and a heat pump unit. Background Technology

[0002] Currently, with the rapid development of the social economy, global energy consumption is constantly increasing, and the call for the research and adoption of new energy-saving technologies is growing stronger. The recovery of low-grade waste heat and the improvement of its quality are particularly important for reducing the consumption of high-quality energy in industrial production and daily life. Steam, as a power source for industrial production, has been widely used in various industrial sectors such as food, pharmaceuticals, chemicals, seawater desalination, and wastewater treatment. The annual demand from the traditional Chinese medicine extraction and brewing industries alone reaches 360 million tons. Currently, industrial steam mainly comes from industrial boilers. Replacing traditional coal-fired boilers with high-temperature steam electric heat pump units can not only save energy but also reduce air pollution caused by coal-fired boilers.

[0003] As the core component of a heat pump unit, the centrifugal compressor has the advantage of large volumetric flow rate, but also suffers from the disadvantage of small single-stage pressure ratio. When water is used as the refrigerant, it outputs steam above 120°C. During operation, the stator temperature of the motor is significantly high. Conventional stator cooling solutions use fans to generate cold air to cool the stator, but the cooling effect is poor and the heat cannot be effectively dissipated, resulting in high motor cavity temperature and low motor efficiency of the steam compressor.

[0004] Therefore, how to design a bushing structure for stator cooling of compressors and a heat pump unit that can effectively reduce stator surface temperature and improve motor efficiency is a technical problem that the industry urgently needs to solve. Summary of the Invention

[0005] In view of the problem that conventional stator cooling solutions in the prior art use fans to generate cold air to cool the stator, but the cooling effect is not good and the heat cannot be effectively removed, this invention proposes a bushing structure and heat pump unit for stator cooling of compressors.

[0006] The technical solution of the present invention is to propose a bushing structure for stator cooling of a compressor, which includes a bushing body 1, the bushing body 1 being sleeved on the stator of the compressor, and further includes a first flow channel 2 and a second flow channel 3 symmetrically distributed on the bushing body 1, the first flow channel 2 and the second flow channel 3 being spirally distributed on the surface of the bushing body 1.

[0007] Based on the above-mentioned scheme, the present invention uses a bushing body 1 fitted onto the stator of the compressor, and sets a first flow channel 2 and a second flow channel 3 on the bushing body 1. The cooling water in the first flow channel 2 and the second flow channel 3 can be used to cool the stator of the compressor. The symmetrical distribution design can ensure the uniformity of cooling of the compressor stator. In addition, the design of two flow channels, instead of a single flow channel that introduces cooling water from one side, can realize the introduction of cooling water from both sides, avoiding the problem of poor cooling effect in the later stage when cooling water is introduced from one side.

[0008] Furthermore, the present invention also includes a plurality of turbulence fins 4 disposed in the first flow channel 2 and the second flow channel 3;

[0009] The turbulence fins 4 are evenly distributed on the sidewalls of the first flow channel 2 and the second flow channel 3, and the turbulence fins 4 on the two sidewalls of the same flow channel are staggered.

[0010] Based on the above solution, the present invention can create turbulence in the cooling water by setting turbulence fins 4 in the first flow channel 2 and the second flow channel 3, which can accelerate the flow of cooling water and thus significantly reduce the stator temperature.

[0011] Furthermore, in this invention, a gap is provided between the turbulence fin 4 and the bottom of the first flow channel 2 and the bottom of the second flow channel 3.

[0012] Based on the above solution, the present invention can ensure that while turbulence is generated by the turbulence fins 4, cooling water can pass through the gap below the turbulence fins 4, thus avoiding the problem of the turbulence fins 4 blocking the flow of cooling water.

[0013] Furthermore, in this invention, the first flow channel 2 has a first inlet 21 and a first outlet 22, and the second flow channel 3 has a second inlet 31 and a second outlet 32;

[0014] The first water inlet 21 and the second water inlet 22 are respectively disposed on the left and right sides of the bushing body 1, and the first water outlet 22 and the second water outlet 32 ​​are disposed in the middle of the bushing body 1.

[0015] Based on the above-mentioned solution, the present invention enables cooling water to be introduced from the first inlet 21 and the second inlet 31 on the left and right sides, and discharged from the first outlet 22 and the second outlet 32 ​​in the middle, so as to cool the stator of the entire compressor. This can effectively improve the cooling effect of the compressor stator and avoid the problem that the cooling effect of the compressor stator is good in the early stage but poor in the later stage when cooling water is introduced from one side.

[0016] Furthermore, in this invention, the groove width of the first flow channel 2 is the same as the groove width of the second flow channel 3, and the groove spacing of the first flow channel 2 is the same as the groove spacing of the second flow channel 3.

[0017] Based on the above solution, the present invention can ensure that the structure of the first flow channel 2 and the second flow channel 3 is consistent, thereby ensuring that the cooling effect on both sides of the compressor stator is the same, and avoiding uneven cooling and low motor efficiency caused by flow channel differences.

[0018] Furthermore, in this invention, the groove width of the first flow channel 2 and the groove spacing of the first flow channel 2 satisfy: L1=0.75*L3;

[0019] The groove width of the second flow channel 3 and the groove spacing of the second flow channel 3 satisfy: L2=0.75*L4;

[0020] Wherein, L1 is the groove width of the first flow channel 2, L2 is the groove width of the second flow channel 3, L3 is the groove spacing of the first flow channel 2, and L4 is the groove spacing of the second flow channel 3.

[0021] Based on the above solution, this invention designs the groove width and groove spacing of the first flow channel 2 and the second flow channel 3 to ensure the sidewall strength of the first flow channel 2 and the second flow channel 3, and avoids the problem of damage to the first flow channel 2 and the second flow channel 3 due to the impact of cooling water. At the same time, the design of the groove width also ensures the flow rate of cooling water in the first flow channel 2 and the second flow channel 3, and avoids the problem of insufficient cooling water to achieve the best cooling effect.

[0022] Furthermore, in this invention, the groove depths of the first flow channel 2 and the second flow channel 3 satisfy the following condition with respect to the thickness of the bushing body 1: D1 = 0.3 - 0.4 * D2;

[0023] Wherein, D1 is the groove depth of the first flow channel 2 and the second flow channel 3, and D2 is the thickness of the bushing body 1.

[0024] Based on the above solution, this invention designs the groove depth of the first flow channel 2 and the second flow channel 3 to avoid the problem that the first flow channel 2 and the second flow channel 3 are too close to the inner wall of the cooling jacket, resulting in insufficient strength of the bushing body 1 and causing holes in the bushing body 1 under the impact of cooling water. At the same time, designing the groove depth of the first flow channel 2 and the second flow channel 3 also ensures the flow rate of cooling water in the first flow channel 2 and the second flow channel 3, avoiding the problem that insufficient cooling water will not achieve the best cooling effect.

[0025] Furthermore, the present invention also includes sealing rings 5 ​​disposed on both sides of the bushing body 1, and the sealing rings 5 ​​are disposed on the outer side of the first flow channel 2 and the second flow channel 3.

[0026] Based on the above solution, the present invention ensures the sealing effect on both sides of the bushing body 1 by designing the sealing ring 5, thereby preventing cooling water from entering the compressor motor cavity through the gap between the bushing body 1 and the compressor housing, which could lead to motor burnout.

[0027] Furthermore, in this invention, the outer side of the bushing body 1 is interference-fitted with the housing of the compressor, so that the bushing body 1 is clamped between the stator of the compressor and the housing of the compressor.

[0028] Based on the above solution, the present invention uses an interference fit between the bushing body 1 and the compressor housing to clamp the bushing body 1 between the compressor stator and the compressor housing, thereby achieving a seal for the first flow channel 2 and the second flow channel 3 and preventing cooling water from flowing into the compressor motor cavity, which could lead to motor burnout.

[0029] The present invention also proposes a heat pump unit, which includes a compressor and a bushing structure disposed on the compressor, the bushing structure employing the aforementioned bushing structure for stator cooling of the compressor.

[0030] Compared with the prior art, the present invention has at least the following beneficial effects:

[0031] 1. The present invention improves the uniformity of heat dissipation of the compressor stator by introducing cooling water from the first and second water inlets on the left and right sides through the first and second flow channels symmetrically distributed on the bushing body and avoiding the problem of poor cooling effect in the later stage when cooling water is introduced from one side.

[0032] 2. By introducing turbulence fins, this invention enables the cooling water to form turbulence, accelerates the flow of cooling water, significantly reduces the stator temperature, and ensures the cooling effect.

[0033] 3. By designing sealing rings on the left and right sides of the bushing body 1, the present invention achieves a sealing effect on the cooling water, preventing the cooling water from entering the motor cavity and causing the motor to burn out, thus ensuring the reliability of motor operation. Attached Figure Description

[0034] To more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0035] Figure 1 This is a schematic diagram of the bushing structure used for stator cooling of the compressor in this invention;

[0036] Figure 2This is a schematic diagram of the bushing structure for stator cooling of the compressor in this invention from a first perspective.

[0037] Figure 3 This is a schematic diagram showing the arrangement of the turbulence-inducing fins in the first and second flow channels of the present invention;

[0038] Figure 4 This is a schematic diagram showing the height design of the turbulence fins in the first and second flow channels of the present invention.

[0039] Figure 5 This is a schematic diagram of the structure of the first flow channel in this invention;

[0040] Figure 6 This is a schematic diagram of the design of the groove width and groove spacing in the first flow channel of the present invention;

[0041] Figure 7 This is a schematic diagram of the structure of the second flow channel in this invention;

[0042] Figure 8 This is a schematic diagram of the design of the groove width and groove spacing in the second flow channel of the present invention;

[0043] Figure 9 This is a schematic diagram of the groove depth design for the first and second flow channels in this invention;

[0044] Figure 10 This is a schematic diagram of the bushing structure for stator cooling of the compressor in this invention from a second perspective.

[0045] Among them, 1 is the bushing body, 2 is the first flow channel, 3 is the second flow channel, 4 is the turbulence fin, and 5 is the sealing ring;

[0046] 21 is the first water inlet, 31 is the second water inlet, 22 is the second water inlet, and 32 is the second water outlet. Detailed Implementation

[0047] To make the technical problems to be solved, the technical solutions, and the beneficial effects of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and are not intended to limit the present invention.

[0048] Therefore, a feature pointed out in this specification is used to describe one feature of one embodiment of the invention, and does not imply that every embodiment of the invention must have the described feature. Furthermore, it should be noted that this specification describes many features. While certain features may be combined to illustrate possible system designs, these features may also be used in other combinations not explicitly stated. Therefore, unless otherwise stated, the described combinations are not intended to be limiting.

[0049] The principles and structure of the present invention will be described in detail below with reference to the accompanying drawings and embodiments.

[0050] Currently, conventional stator cooling solutions use fans to generate cold air to cool the stator. This method is ineffective and fails to effectively dissipate heat, leading to high motor cavity temperatures and reduced motor efficiency. To address these issues, this invention proposes a bushing structure for compressor stator cooling. The bushing structure is fitted onto the compressor stator, and cooling water is used to cool the stator through flow channels within the bushing structure.

[0051] Please see the appendix Figure 1 Appendix Figure 2 and appendix Figure 10 The bushing structure for cooling the stator of a compressor proposed in this invention includes a bushing body 1, which is a hollow cylinder with an inner diameter that matches the stator of the compressor and is used to be fitted onto the stator of the compressor.

[0052] A first flow channel 2 and a second flow channel 3 are distributed on the bushing body 1. The first flow channel 2 and the second flow channel 3 are symmetrically distributed about the centerline of the bushing body 1, and both the first flow channel 2 and the second flow channel 3 are spirally distributed on the surface of the bushing body 1.

[0053] In some existing solutions that use cooling water to cool the compressor stator, a single flow channel is typically used to introduce cooling water from one side to cool the compressor stator. While this design provides good cooling at the beginning of the flow channel, the cooling effect may be poor at the end due to insufficient cooling water flow rate or velocity. In this invention, a dual-flow channel design is adopted, which shortens the total flow of a single flow channel and avoids the problems of insufficient cooling water flow rate or velocity at the end of the flow channel, thereby improving the cooling effect on the compressor stator.

[0054] To further solve the problem of uneven cooling of the compressor stator, the present invention designs the first flow channel 1 and the second flow channel 2 symmetrically to make the cooling water flow rate and velocity on both sides equal, so as to ensure that the compressor stator has the same cooling effect in the first flow channel 1 and the second flow channel 2, thus avoiding the problem of uneven cooling of the compressor stator.

[0055] In addition, to improve the cooling effect of the cooling water on the compressor stator, the first flow channel 2 and the second flow channel 3 are spirally distributed in this invention. Under this design, the first flow channel 2 and the second flow channel 3 can almost completely cover the entire part of the compressor stator, increasing the heat exchange area between the cooling water and the compressor stator, and ensuring the cooling effect of the cooling water on the compressor stator.

[0056] In other words, based on the above-mentioned scheme, the present invention uses a bushing body 1 fitted onto the stator of the compressor, and sets a first flow channel 2 and a second flow channel 3 on the bushing body 1. The cooling water in the first flow channel 2 and the second flow channel 3 can be used to cool the stator of the compressor. The symmetrical distribution design can ensure the uniformity of cooling of the compressor stator. Moreover, the design of two flow channels, rather than a single flow channel that introduces cooling water from one side, can achieve the introduction of cooling water from both sides, avoiding the problem of poor cooling effect in the later stage when cooling water is introduced from one side.

[0057] The present invention also includes a plurality of turbulence fins 4 disposed in the first flow channel 2 and the third flow channel 3;

[0058] The turbulence fins 4 are evenly distributed on the sidewalls of the first flow channel 2 and the second flow channel 3, and the turbulence fins 4 on the two sidewalls of the same flow channel are staggered.

[0059] Since the first flow channel 2 and the second flow channel 3 are symmetrically distributed, and the arrangement of the baffle fins 4 is the same for both, the present invention will be described here with reference to the arrangement of the baffle fins 4 on the first flow channel 2. Please refer to the appendix. Figure 3 This is a simplified schematic diagram of the first flow channel 2. The left and right sides represent the two side walls of the first flow channel 2, respectively. The turbulence fins 4 are multiple small protrusions set on the first flow channel 2. When the cooling water passes through, due to the turbulence of the turbulence fins 4, turbulence will be formed at the turbulence fins 4, thereby accelerating the flow rate of the cooling water and improving the cooling effect.

[0060] The present invention has a first flow channel 2 and a second flow channel 3. The turbulence fins 4 are distributed in the first flow channel 2 and the second flow channel 3 in a consistent manner to ensure that the cooling effect of the cooling water at the first flow channel 2 is consistent with the cooling effect at the second flow channel 3, thereby achieving uniform cooling of the compressor stator.

[0061] Each flow channel has two sidewalls, and the turbulence fins 4 are set on the sidewalls. In order to ensure that the turbulence fins 4 do not completely obstruct the flow of cooling water, the present invention distributes the turbulence fins 4 in a staggered manner on the two sidewalls of the same flow channel. Specifically, the staggered distribution means that after the turbulence fins 4 are set on one sidewall, the next turbulence fin 4 is set on the other sidewall, so as to avoid the simultaneous setting of turbulence fins 4 on the two sidewalls of the same part.

[0062] In this way, when the cooling water flows through the turbulence fins 4 on one side wall, turbulence is formed, which can pass through the gap between the turbulence fins 4 and the other side wall, thus avoiding blockage of the cooling water flow.

[0063] In other words, based on the above solution, the present invention can create turbulence in the cooling water by setting turbulence fins 4 in the first flow channel 2 and the second flow channel 3, thereby accelerating the flow of cooling water and significantly reducing the stator temperature.

[0064] In this invention, when turbulence fins 4 are provided on the sidewalls of the first flow channel 2 and the second flow channel 3, a gap is provided between the turbulence fins 4 and the bottom of the first flow channel 2 and the bottom of the second flow channel 3.

[0065] Since the first flow channel 2 and the second flow channel 3 are symmetrically distributed, and the arrangement of the baffle fins 4 is the same for both, the present invention will be described here with reference to the arrangement of the baffle fins 4 on the first flow channel 2. Please refer to the appendix. Figure 4 This is a simplified schematic diagram of the first flow channel 2. The left and right sides represent the two sidewalls of the first flow channel 2, respectively. The turbulence fins 4 are small protrusions provided on the sidewalls of the first flow channel 2, located at the top of the sidewalls. A certain gap is provided between the bottom of the turbulence fins 4 and the bottom of the first flow channel 2, i.e., attached... Figure 4 The spacing d in the middle allows the cooling water to flow through the gap below the turbulence fin 4 without being blocked by the turbulence fin 4.

[0066] Similarly, the design of the turbulence fins 4 on the second flow channel 3 is such that they are set at the top of the side wall of the second flow channel 3, and a certain gap is set between the bottom of the turbulence fins 4 and the bottom of the first flow channel 2. When the cooling water flows through, it can flow through the gap below the turbulence fins 4 and will not be blocked by the turbulence fins 4.

[0067] In other words, based on the above solution, the present invention can ensure that while turbulence is generated by the turbulence fins 4, cooling water can pass through the gap below the turbulence fins 4, thus avoiding the problem of the turbulence fins 4 blocking the flow of cooling water.

[0068] Please see the appendix Figure 2 and appendix Figure 5 In this invention, the first flow channel 2 has a first inlet 21 and a second outlet 22;

[0069] The first water inlet 21 is located on the top left side of the bushing body 1 for introducing cooling water, and the first water outlet 22 is located in the middle of the bushing body 1 for discharging cooling water.

[0070] Please see the appendix Figure 2 and appendix Figure 7 To adapt to the design of the first flow channel 2, the present invention provides a second flow channel 3 with a second inlet 31 and a second outlet 32. The second inlet 31 is located on the top right side of the bushing body 1 for introducing cooling water, and the second outlet 32 ​​is located in the middle of the bushing body 1 for discharging cooling water.

[0071] Here, the second inlet 31 and the second outlet 32 ​​of the second flow channel 2 are matched with the positions of the first inlet 21 and the first outlet 22 to ensure the symmetrical design of the first flow channel 2 and the second flow channel 3, so that the cooling water can cool the stator of the compressor evenly.

[0072] In some existing solutions that use cooling water to cool the compressor stator, a single flow channel is typically used to introduce cooling water from one side to cool the compressor stator. While this design provides good cooling at the beginning of the flow channel, the cooling effect may be poor at the end due to insufficient cooling water flow rate or velocity. In this design, the end of the flow channel is generally located on both sides of the compressor stator. If the inlet is placed on the left side of the compressor stator and the outlet on the right side, the end of the flow channel will be on the right side of the compressor stator, resulting in poor cooling. Similarly, if the inlet is placed on the right side of the compressor stator and the outlet on the left side, the end of the flow channel will be on the left side of the compressor stator, resulting in poor cooling.

[0073] Under normal circumstances, the water flow rate and velocity at the inlet and outlet are relatively high. By setting the first water inlet 21 and the second water inlet 31 on the left and right sides of the bushing body 1 respectively, this invention can ensure the cooling effect on both sides of the compressor stator and avoid the problem of poor cooling effect on both sides of the compressor stator.

[0074] In other words, based on the above-mentioned solution, the present invention enables cooling water to be introduced from the first inlet 21 and the second inlet 31 on the left and right sides, and discharged from the first outlet 22 and the second outlet 32 ​​in the middle, so as to cool the stator of the entire compressor. This can effectively improve the cooling effect of the compressor stator and avoid the problem that the cooling effect of the compressor stator is good in the early stage but poor in the later stage when cooling water is introduced from one side.

[0075] In other embodiments of the present invention, the first flow channel 2 has a first inlet 21 and a second outlet 22;

[0076] The first water inlet 21 is located at the bottom left side of the bushing body 1 for introducing cooling water, and the first water outlet 22 is located in the middle of the bushing body 1 for discharging cooling water.

[0077] To accommodate the design of the first flow channel 2, the present invention provides a second flow channel 3 with a second inlet 31 and a second outlet 32. The second inlet 31 is located at the bottom right side of the bushing body 1 for introducing cooling water, and the second outlet 32 ​​is located in the middle of the bushing body 1 for discharging cooling water.

[0078] Here, the second inlet 31 and the second outlet 32 ​​of the second flow channel 2 are matched with the positions of the first inlet 21 and the first outlet 22 to ensure the symmetrical design of the first flow channel 2 and the second flow channel 3, so that the cooling water can cool the stator of the compressor evenly.

[0079] This embodiment, compared to the appendix Figure 5and appendix Figure 7 In this embodiment, the first water inlet 21 is located at the bottom left side, the second water inlet 31 is located at the bottom right side, and the design of the first water outlet 22 and the second water outlet 32 ​​is completely identical, which can achieve the same technical effect as the above embodiment.

[0080] In some existing solutions that use cooling water to cool the compressor stator, a single flow channel is typically used to introduce cooling water from one side to cool the compressor stator. While this design provides good cooling at the beginning of the flow channel, the cooling effect may be poor at the end due to insufficient cooling water flow rate or velocity. In this design, the end of the flow channel is generally located on both sides of the compressor stator. If the inlet is placed on the left side of the compressor stator and the outlet on the right side, the end of the flow channel will be on the right side of the compressor stator, resulting in poor cooling. Similarly, if the inlet is placed on the right side of the compressor stator and the outlet on the left side, the end of the flow channel will be on the left side of the compressor stator, resulting in poor cooling.

[0081] Under normal circumstances, the water flow rate and velocity at the inlet and outlet are relatively high. By setting the first water inlet 21 and the second water inlet 31 on the left and right sides of the bushing body 1 respectively, this invention can ensure the cooling effect on both sides of the compressor stator and avoid the problem of poor cooling effect on both sides of the compressor stator.

[0082] In other words, based on the above-mentioned solution, the present invention enables cooling water to be introduced from the first inlet 21 and the second inlet 31 on the left and right sides, and discharged from the first outlet 22 and the second outlet 32 ​​in the middle, so as to cool the stator of the entire compressor. This can effectively improve the cooling effect of the compressor stator and avoid the problem that the cooling effect of the compressor stator is good in the early stage but poor in the later stage when cooling water is introduced from one side.

[0083] Please see the appendix Figure 6 To be continued Figure 8 In this invention, when setting the groove width and groove spacing of the first flow channel 2 and the groove width and groove spacing of the second flow channel 3, the groove width of the first flow channel 2 is set to be consistent with the groove width of the second flow channel 3, and the groove spacing of the first flow channel 2 is consistent with the groove spacing of the second flow channel 3.

[0084] Here, the width of the first flow channel 2 refers to the distance between the two side walls of the first flow channel 2, that is, the width through which the cooling water can flow. (See attached diagram.) Figure 6 The spacing L1 in the middle, the slot pitch of the first flow channel 2 refers to the distance between two adjacent first flow channels 2 when the first flow channel 2 is spirally distributed (referring to the distance between one sidewall of the first first flow channel 2 and the corresponding sidewall of the adjacent first flow channel 2), corresponding to the attached Figure 6 The spacing L3 in the middle;

[0085] The width of the second flow channel 3 refers to the distance between the two side walls of the second flow channel 3, that is, the width through which cooling water can flow. Figure 8 The spacing L2 in the middle, the slot pitch of the second flow channel 3 refers to the distance between two adjacent second flow channels 3 when the second flow channels 3 are spirally distributed (referring to the distance between one sidewall of the first second flow channel 3 and the corresponding sidewall of the adjacent second flow channel 3), corresponding to the attached Figure 8 The spacing L4 in the middle;

[0086] The present invention sets the groove width of the first flow channel 2 to be consistent with the groove width of the second flow channel 3, and sets the groove spacing of the first flow channel 2 to be consistent with the groove spacing of the second flow channel 3. This is to ensure the consistency between the first flow channel 2 and the second flow channel 3, so as to ensure uniform cooling of the compressor stator by the cooling water.

[0087] Please see the appendix Figure 5 and appendix Figure 6 In this invention, when setting the groove width and groove spacing of the first flow channel 2, the groove width and groove spacing of the first flow channel 2 are set to satisfy: L1=0.75*L3;

[0088] Where L1 is the groove width of the first flow channel 2, and L3 is the groove spacing of the first flow channel 2;

[0089] From the appendix Figure 6 It can be clearly seen that the difference between the groove width and the groove spacing is essentially the sidewall thickness of the first flow channel 2. Theoretically, the wider the groove width of the first flow channel 2, the greater the flow rate of cooling water that can flow through, and the better the cooling effect. However, it will also result in a thinner sidewall thickness of the first flow channel 2, which may cause the first flow channel 2 to fail to meet the processing and strength requirements, or even breakage under the impact of cooling water. Therefore, when designing the groove width and groove spacing of the first flow channel 2, it is necessary to comprehensively consider the cooling water flow rate, i.e., the cooling effect, as well as the installation strength of the first flow channel 2. In this invention, by reasonably setting the groove width and groove spacing of the first flow channel 2, the groove width and groove spacing of the first flow channel 2 satisfy: L1=0.75*L3;

[0090] Under this design, both the flow rate of cooling water in the first flow channel 2 and the installation strength of the first flow channel 2 can be guaranteed. That is, based on the above scheme, the present invention ensures the side wall strength of the first flow channel 2 by designing the groove width and groove spacing of the first flow channel 2, avoiding the problem of damage to the first flow channel 2 caused by cooling water impact. At the same time, the design of the groove width also ensures the flow rate of cooling water in the first flow channel 2, avoiding the problem of insufficient cooling water to achieve the best cooling effect.

[0091] Please see the appendix Figure 7 and appendix Figure 8In this invention, when setting the groove width and groove spacing of the second flow channel 3, the present invention sets them to satisfy: L2=0.75*L4;

[0092] Where L2 is the groove width of the second flow channel 3, and L4 is the groove spacing of the second flow channel 3;

[0093] From the appendix Figure 6 It can be clearly seen that the difference between the groove width and the groove spacing is essentially the sidewall thickness of the second flow channel 3. Theoretically, the wider the groove width of the second flow channel 3, the greater the flow rate of cooling water that can flow through, and the better the cooling effect. However, it will also result in a thinner sidewall thickness of the second flow channel 3, which may cause the second flow channel 3 to fail to meet the processing and strength requirements, or even breakage under the impact of cooling water. Therefore, when designing the groove width and groove spacing of the second flow channel 3, it is necessary to comprehensively consider the cooling water flow rate, i.e., the cooling effect, as well as the installation strength of the second flow channel 3. In this invention, by reasonably setting the groove width and groove spacing of the second flow channel 3, the groove width and groove spacing of the second flow channel 3 satisfy: L2=0.75*L4;

[0094] Under this design, both the water flow rate of the cooling water in the second flow channel 3 and the installation strength of the second flow channel 3 can be guaranteed. That is, based on the above scheme, the present invention ensures the side wall strength of the second flow channel 3 by designing the groove width and groove spacing, avoiding the problem of damage to the second flow channel 3 due to cooling water impact. At the same time, the design of the groove width also ensures the flow rate of the cooling water in the second flow channel 3, avoiding the problem of insufficient cooling water to achieve the best cooling effect.

[0095] Please see the appendix Figure 9 In this invention, when setting the first flow channel 2, the groove depth of the first flow channel 2 and the thickness of the bushing body 1 are set to satisfy: D1=0.3-0.4*D2;

[0096] Where D1 is the groove depth of the first flow channel 2, and D2 is the thickness of the bushing body 1;

[0097] Here, the depth of the first flow channel 2 can reflect the distance between the cooling water and the stator of the compressor. The deeper the first flow channel 2, the smaller the distance between the cooling water and the stator of the compressor, and the better the cooling effect on the stator of the compressor. In addition, the deeper the first flow channel 2, the higher the flow rate of the cooling water, and the better the cooling effect on the stator of the compressor.

[0098] However, increasing the groove depth of the first flow channel 2 will reduce the thickness of the bushing body 1 at the first flow channel 2, resulting in insufficient structural strength of the bushing body 1. Under the impact of cooling water pressure, it may cause holes to appear in the first flow channel 2, allowing cooling water to enter the motor cavity, causing the motor to burn out and the compressor to fail to operate normally.

[0099] Therefore, when setting the groove depth of the first flow channel 2, the present invention needs to comprehensively consider the cooling effect of the cooling water and the strength of the bushing body 1. To this end, the groove depth of the first flow channel 2 and the thickness of the bushing body 1 are set as follows: D1=0.3-0.4*D2, which can improve the cooling effect of the cooling water as much as possible while ensuring the structural strength of the bushing body 1.

[0100] In this invention, when setting the second flow channel 3, the groove depth of the second flow channel 3 and the thickness of the bushing body 1 are set to satisfy: D1=0.3-0.4*D2;

[0101] Where D1 is the groove depth of the second flow channel 3, and D2 is the thickness of the bushing body 1;

[0102] Here, the depth of the second flow channel 3 can reflect the distance between the cooling water and the stator of the compressor. The deeper the second flow channel 3, the smaller the distance between the cooling water and the stator of the compressor, and the better the cooling effect on the stator of the compressor. In addition, the deeper the second flow channel 3, the higher the flow rate of the cooling water, and the better the cooling effect on the stator of the compressor.

[0103] However, increasing the groove depth of the second flow channel 3 will reduce the thickness of the bushing body 1 at the second flow channel 3, resulting in insufficient structural strength of the bushing body 1. Under the impact of cooling water pressure, it may cause holes to appear in the second flow channel 3, allowing cooling water to enter the motor cavity, causing the motor to burn out and the compressor to fail to operate normally.

[0104] Therefore, when setting the groove depth of the second flow channel 3, the present invention needs to comprehensively consider the cooling effect of the cooling water and the strength of the bushing body 1. To this end, the groove depth of the second flow channel 3 and the thickness of the bushing body 1 are set as follows: D1=0.3-0.4*D2, which can improve the cooling effect of the cooling water as much as possible while ensuring the structural strength of the bushing body 1.

[0105] In other words, based on the above-mentioned solution, the present invention designs the groove depth of the first flow channel 2 and the second flow channel 3 to avoid the problem that the first flow channel 2 and the second flow channel 3 are too close to the inner wall of the cooling jacket, resulting in insufficient strength of the bushing body 1 and causing holes in the bushing body 1 under the impact of cooling water. At the same time, designing the groove depth of the first flow channel 2 and the second flow channel 3 also ensures the flow rate of cooling water in the first flow channel 2 and the second flow channel 3, avoiding the problem that insufficient cooling water will not achieve the best cooling effect.

[0106] Please see the appendix Figure 1 and appendix Figure 2 The present invention also includes sealing rings 5 ​​disposed on both sides of the bushing body 1, and the sealing rings 5 ​​are disposed on the outside of the first flow channel 2 and the second flow channel 3.

[0107] Here, the sealing ring 5 is O-shaped and is mainly used to seal the cooling water on the left and right sides. It is used to prevent cooling water from entering the compressor motor cavity from the gap between the bushing body 1 and the compressor housing, which could cause the motor to burn out.

[0108] In other words, based on the above solution, the present invention ensures the sealing effect on the left and right sides of the bushing body 1 through the design of the sealing ring 5, and avoids the problem of cooling water entering the compressor motor cavity from the gap between the bushing body 1 and the compressor housing, which would cause the motor to burn out.

[0109] Furthermore, when setting the bushing body 1, the present invention also makes an interference fit between the outer side of the bushing body 1 and the compressor housing, so that the bushing body 1 is clamped between the compressor stator and the compressor housing.

[0110] The design mainly utilizes the compressor housing to seal the first flow channel 2 and the second flow channel 3, preventing cooling water from entering the compressor's motor cavity.

[0111] In other words, based on the above solution, the present invention uses an interference fit between the bushing body 1 and the compressor housing to clamp the bushing body 1 between the compressor stator and the compressor housing, thereby achieving a seal for the first flow channel 2 and the second flow channel 3 and preventing cooling water from flowing into the compressor motor cavity, which could lead to motor burnout.

[0112] Based on the above design, the present invention also proposes a heat pump unit, which includes a compressor and a bushing structure disposed on the compressor, the bushing structure adopting the aforementioned bushing structure for stator cooling of the compressor.

[0113] Compared with the prior art, the present invention has at least the following beneficial effects:

[0114] 1. The present invention improves the uniformity of heat dissipation of the compressor stator by introducing cooling water from the first and second water inlets on the left and right sides through the first and second flow channels symmetrically distributed on the bushing body and avoiding the problem of poor cooling effect in the later stage when cooling water is introduced from one side.

[0115] 2. By introducing turbulence fins, this invention enables the cooling water to form turbulence, accelerates the flow of cooling water, significantly reduces the stator temperature, and ensures the cooling effect.

[0116] 3. By designing sealing rings on the left and right sides of the bushing body 1, the present invention achieves a sealing effect on the cooling water, preventing the cooling water from entering the motor cavity and causing the motor to burn out, thus ensuring the reliability of motor operation.

[0117] It should be noted that the terminology used above is for describing specific embodiments only and is not intended to limit the exemplary embodiments of the present invention. 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. The order of execution of actions, steps, etc., in the apparatus and methods described in the specification and drawings can be implemented in any order unless a specific order is expressly specified, and as long as the output of the preceding process is not used in the subsequent process. Similar sequential terms used for ease of description do not imply that such an order must be followed.

[0118] Techniques, methods, and apparatus known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and apparatus 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 constraints. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0119] The above description is only 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.

Claims

1. A bushing structure for stator cooling of a compressor, comprising a bushing body (1), the bushing body (1) being sleeved on the stator of the compressor, characterized in that, It also includes a first flow channel (2) and a second flow channel (3) symmetrically distributed on the bushing body (1), and the first flow channel (2) and the second flow channel (3) are spirally distributed on the surface of the bushing body (1).

2. The bushing structure for stator cooling of a compressor according to claim 1, characterized in that, It also includes a plurality of turbulence fins (4) disposed in the first flow channel (2) and the second flow channel (3); The turbulence fins (4) are evenly distributed on the sidewalls of the first flow channel (2) and the second flow channel (3), and the turbulence fins (4) on the two sidewalls of the same flow channel are staggered.

3. The bushing structure for stator cooling of a compressor according to claim 2, characterized in that, The turbulence fins (4) are provided with gaps between the bottom of the first flow channel (2) and the bottom of the second flow channel (3).

4. The bushing structure for stator cooling of a compressor according to claim 1, characterized in that, The first flow channel (2) has a first inlet (21) and a first outlet (22), and the second flow channel (3) has a second inlet (31) and a second outlet (32). The first water inlet (21) and the second water inlet (22) are respectively located on the left and right sides of the bushing body (1), and the first water outlet (22) and the second water outlet (32) are located in the middle of the bushing body (1).

5. The bushing structure for stator cooling of a compressor according to claim 1, characterized in that, The width of the first flow channel (2) is the same as the width of the second flow channel (3), and the spacing between the slots of the first flow channel (2) is the same as the spacing between the slots of the second flow channel (3).

6. The bushing structure for stator cooling of a compressor according to claim 4, characterized in that, The width of the first flow channel (2) and the spacing between the first flow channels (2) satisfy: L1=0.75*L3; The groove width of the second flow channel (3) and the groove spacing of the second flow channel (3) satisfy: L2=0.75*L4; Wherein, L1 is the groove width of the first flow channel (2), L2 is the groove width of the second flow channel (3), L3 is the groove spacing of the first flow channel (2), and L4 is the groove spacing of the second flow channel (3).

7. The bushing structure for stator cooling of a compressor according to claim 1, characterized in that, The groove depths of the first flow channel (2) and the second flow channel (3) satisfy the following condition with respect to the thickness of the bushing body (1): D1 = 0.3 - 0.4 * D2; Wherein, D1 is the groove depth of the first flow channel (2) and the second flow channel (3), and D2 is the thickness of the bushing body (1).

8. The bushing structure for stator cooling of a compressor according to claim 1, characterized in that, It also includes sealing rings (5) disposed on both sides of the bushing body (1), and the sealing rings (5) are disposed on the outside of the first flow channel (2) and the second flow channel (3).

9. The bushing structure for stator cooling of a compressor according to claim 1, characterized in that, The outer side of the bushing body (1) is interference-fitted with the housing of the compressor so that the bushing body (1) is clamped between the stator of the compressor and the housing of the compressor.

10. A heat pump unit, comprising a compressor, characterized in that, It also includes a bushing structure disposed on the compressor, the bushing structure being a bushing structure for stator cooling of the compressor as described in any one of claims 1 to 9.

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