Rotary compressor for use in a flash freezer

Abstract

A rotary compressor for use in a flash freezer is provided. The rotary compressor can be used to charge a refrigerant selected from one of R1270 and R290. The rotary compressor includes a pump having a first longitudinal axis, a ring having a second longitudinal axis, and a shaft extending through the ring. The pump includes an upper bearing, a cylinder, a lower bearing, and a vane. The cylinder has a suction port and the suction port can be used to draw in the refrigerant. The upper bearing has a discharge port and can be used to discharge the refrigerant. The discharge port has a thickness of no more than 2 millimeters and the discharge port has an effective area of between 28 square millimeters and 51 square millimeters. The ring has a height-to-radius ratio of between 1.4 and 1.7. The shaft is rotatable relative to the first longitudinal axis to cause the ring to rotate relative to the pump.

Description

Technical Field

[0001] This invention relates to a rotary compressor, and more particularly to a rotary compressor for use in rapid refrigeration appliances. Background Technology

[0002] In the field of refrigeration technology, existing refrigeration systems typically use reciprocating compressors in conjunction with refrigerants. However, reciprocating compressors compress the refrigerant through the reciprocating motion of a piston, resulting in a slow pressure build-up process, making it difficult to achieve rapid cooling effects.

[0003] Therefore, the inventor believed that the above-mentioned defects could be improved, and thus devoted himself to research and applied scientific principles, and finally proposed an invention that is reasonably designed and effectively improves the above-mentioned defects. Summary of the Invention

[0004] Therefore, the technical problem to be solved by the present invention is to provide a rotary compressor for rapid freezing appliances, which addresses the shortcomings of the prior art.

[0005] To achieve the aforementioned objective, this invention discloses a rotary compressor for use in rapid freezing appliances, wherein the rotary compressor is capable of adding a refrigerant selected from R1270 and R290; the rotary compressor includes: a pump having a first longitudinal axis, the pump comprising: an upper support having a discharge port having a depth of no more than 2 mm and an effective area between 28 square millimeters and 51 square millimeters; wherein the discharge port is capable of discharging the refrigerant; a cylinder connected to the upper support, the cylinder having a suction port capable of drawing in the refrigerant. The refrigerant; and a lower support disposed on a side away from the upper support, wherein the upper support, the cylinder, and the lower support together form a chamber; a ring having a second longitudinal axis parallel to and spaced from the first longitudinal axis, and the ring being disposed within the pump; wherein the ring has a height-to-radius ratio between 1.4 and 1.7; a shaft passing through and contacting the ring along the first longitudinal axis; the shaft being rotatable relative to the first longitudinal axis so that the ring is rotatable relative to the pump; and a blade extending from the outside of the pump into the chamber, and the blade being contacting the outer surface of the ring.

[0006] Preferably, the shaft further includes a cam located within the cavity, and the cam is capable of contacting an inner side surface of the ring; the cam has a height not exceeding 24 mm.

[0007] Preferably, the height of the cam is between 10 mm and 16 mm.

[0008] Preferably, the portion of the shaft excluding the cam has a minimum radius of no more than 9 mm relative to the first longitudinal axis.

[0009] Preferably, the displacement of the rotary compressor is between 13.5 cc and 26 cc.

[0010] Preferably, the displacement of the rotary compressor is between 15 cc and 18 cc.

[0011] Preferably, the rotary compressor further includes an oil body selected from a PAG type oil and a POE type oil; the PAG type oil has a kinematic viscosity between 90 cSt and 110 cSt at a temperature of 40°C, and the POE type oil has a kinematic viscosity between 62 cSt and 74 cSt at a temperature of 40°C.

[0012] Preferably, the oil volume has an oil quantity between 150 cc and 270 cc.

[0013] In summary, the rotary compressor for rapid freezing appliances disclosed in the embodiments of the present invention can achieve this by selecting specific refrigerants such as R1270 or R290, and by having a discharge port with a diameter of 28 square millimeters (mm²). 2 The design of the effective area of ​​51 square millimeters reduces the pressure drop when the refrigerant of R1270 or R290 passes through the valve (e.g., a flow restrictor), thereby effectively improving the operating efficiency of the rotary compressor and simultaneously improving the refrigeration efficiency.

[0014] To further understand the features and technical content of this invention, please refer to the following detailed description and accompanying drawings. However, these descriptions and drawings are only for illustrating the invention and are not intended to limit the scope of protection of the invention in any way. Attached Figure Description

[0015] Figure 1 This is a system schematic diagram of the rapid freezing appliance according to an embodiment of the present invention.

[0016] Figure 2 This is a schematic cross-sectional view of the rotary compressor along the axial direction according to an embodiment of the present invention.

[0017] Figure 3 This is a cross-sectional schematic diagram of a rotary compressor along the radial direction according to an embodiment of the present invention.

[0018] Symbol explanation: Detailed Implementation

[0019] To understand the features, content, advantages, and effects of the present invention, the present invention is described in detail below with reference to the accompanying drawings and embodiments. The drawings used are for illustrative purposes only and to assist in the description. They may not represent the actual proportions and precise configurations of the present invention after implementation. Therefore, the proportions and configurations of the accompanying drawings should not be used to interpret or limit the scope of the present invention in actual implementation.

[0020] The advantages, features, and technical methods of this invention will be more readily understood by referring to the exemplary embodiments and accompanying drawings. This invention may be implemented in different forms and should not be construed as being limited to the embodiments set forth herein. Rather, the embodiments provided will enable those skilled in the art to more thoroughly and completely convey the scope of this invention, which will be defined only by the appended claims.

[0021] Please see Figures 1 to 3 As shown, this embodiment discloses a rapid freezing appliance 201, which includes a rotary compressor 100, a refrigerant pipe 202 connected to the rotary compressor 100, a condenser 203 (e.g., a tube-fin condenser) connected to the refrigerant pipe 202, a filter 204 connected to the condenser 203, a capillary tube C1 connected to the filter 204, a flow restrictor 205 (e.g., a valve) connected to the capillary tube C1, a capillary tube C2 connected to the flow restrictor 205, an evaporator 206 connected to the flow restrictor 205, and a plurality of fans 207, but the present invention is not limited thereto. For example, the rotary compressor 100 may be used alone (e.g., implemented, manufactured, sold, etc.) or used in conjunction with other components.

[0022] In other words, such as Figure 1 As shown, the condenser 203, the filter 204, the flow restrictor 205, the evaporator 206, and the rotary compressor 100 can be connected in series from the refrigerant pipe 202 to form a refrigerant R path. Furthermore, in other embodiments not shown in this invention, the rotary compressor 100 can be applied not only to the rapid freezing appliance 201, but also to a heat pump system, etc., and this invention does not impose any limitations on these applications.

[0023] In practice, the rapid freezing appliance 201 can be further applied to household appliances. That is, the household appliance includes the rapid freezing appliance 201, and in this embodiment, the household appliance is an ice cream maker, but the invention is not limited thereto. For example, the household appliance can be a refrigerator, air conditioner, water dispenser, or ice water / ice cube processor, etc.

[0024] It should be noted that the rotary compressor 100 can be used to add a refrigerant R (e.g., a combustible refrigerant), and the refrigerant R is selected from R1270 and R290. However, the selection of the refrigerant can be adjusted and changed according to design requirements, and the present invention is not limited thereto. Furthermore, in this embodiment, by using a specific refrigerant R of R1270 or R290, the rotary compressor 100 can effectively improve its refrigeration efficiency.

[0025] Among them, such as Figure 2 and Figure 3 As shown, the rotary compressor 100 includes a pump 1 having a first longitudinal axis L1, a ring 2 disposed within the pump 1, a shaft 3 passing through and contacting the ring 2 along the first longitudinal axis L1, and a blade 4 disposed within the pump 1.

[0026] To facilitate understanding of this embodiment, the structure of each component in the rotary compressor 100 will be described in sequence below, and the matching relationship between the components will be explained as appropriate. (See reference below.) Figure 2 As shown, the pump 1 includes an upper support 11, a cylinder 12 connected to the upper support 11, and a lower support 13 disposed on a side away from the upper support 11, and the upper support 11, the cylinder 12 and the lower support 13 can together form a chamber A.

[0027] The cylinder 12 has an intake port 121 for drawing in the refrigerant R. The upper support 11 has an outlet port 111 for discharging the refrigerant R. Furthermore, the outlet port 111 has a depth d along the first longitudinal axis L1, and the depth d is not greater than 2 millimeters (mm).

[0028] More specifically, the outlet 111 has a first area relative to the lower support 13, and the outlet 111 has a size of between 28 square millimeters (mm²). 2 An effective area Q of 51 square millimeters. It should be noted that the effective area Q is the portion of the first area of ​​the outlet 111 that is not covered by the cylinder body 12.

[0029] It is worth mentioning that, in this embodiment, the cylinder body 12 is further recessed with a recess 122 to avoid the cylinder body 12 from blocking the outlet 111, thereby making the effective area Q almost equal to the first area. However, the configuration relationship between the cylinder body 12 and the outlet 111 of the lower support 13 can be adjusted and changed according to design requirements, and the present invention is not limited thereto.

[0030] Furthermore, by increasing the effective area Q of the outlet 111, the pressure drop of the refrigerant R when passing through the valve (e.g., a flow restrictor) can be reduced, thereby reducing energy loss (e.g., motor loss) and further improving the operating efficiency of the rotary compressor 100 (i.e., improving refrigeration efficiency). In other words, the rotary compressor 100 can reduce the pressure drop of the refrigerant R when passing through the valve (e.g., a flow restrictor) by increasing the effective area Q of the outlet 111, thereby improving the refrigeration efficiency of the rotary compressor 100.

[0031] Re-reference Figure 2 and Figure 3 As shown, the ring 2 has a second longitudinal axis L2 that is parallel to and spaced from the first longitudinal axis L1, and the ring 2 is eccentrically positioned relative to the pump 1 (that is, the ring 2 is centered on the second longitudinal axis L2, and the pump 1 is centered on the first longitudinal axis L1).

[0032] Furthermore, the ring 2 has a height-to-radius ratio between 1.4 and 1.7. It should be noted that this height-to-radius ratio is the ratio of a height hr of the ring 2 to a radius rr of an outer surface 22 of the ring 2 relative to the second longitudinal axis L2 (i.e., hr / rr). Additionally, the ring 2 has a contact line K that contacts an inner surface of the cylinder body 12, and the length of the contact line K corresponds to the height hr of the ring 2.

[0033] More specifically, the lower end face 21 of the ring 2 can be supported by the lower support 13, and the lower end face 21 of the ring 2 can move (e.g., rotate) along the lower support 13. Specifically, the ring 2 rotates relative to the pump 1 via the shaft 3.

[0034] Re-reference Figure 2 and Figure 3 As shown, the shaft 3 and the pump 1 are concentrically arranged (that is, both the shaft 3 and the pump 1 can be centered on the first longitudinal axis L1). Further, the shaft 3 is arranged to pass through the upper support 11, the cylinder 12, and the lower support 13, and the upper support 11 is a bushing to provide mounting for the shaft 3.

[0035] Re-reference Figure 2As shown, in this embodiment, the shaft 3 further includes a cam 31 located within the chamber A, and the cam 31 is capable of contacting an inner surface 23 of the ring 2. Further, the cam 31 has a height hc not greater than 24 mm, and the height hc is preferably between 10 mm and 16 mm, but it can be adjusted according to design requirements, and the invention is not limited thereto. More specifically, the shaft 3 has a minimum radius rs relative to the first longitudinal axis L1 not greater than 9 mm (that is, the portion of the shaft 3 excluding the cam 31).

[0036] It should be further noted that the shaft 3 is connected to a motor (not shown). Specifically, when the motor drives the shaft 3 to rotate, the shaft 3 can press the ring 2 against an inner surface of the cylinder 12 via the cam 31, and the cam 31 can drive the ring 2 to rotate along the inner surface of the cylinder 12, but the invention is not limited thereto. For example, in other embodiments of the invention not shown, the shaft 3 may also include a bearing that contacts the ring 2 to rotate relative to the inner surface 23 of the ring 2.

[0037] Furthermore, when the shaft 3 rotates, causing the ring 2 to rotate along the inner surface of the cylinder 12, the contact line K can trace a closed loop. According to the above configuration, when the ring 2 completes one full rotation relative to the inner surface of the cylinder 12 through the shaft 3, the displacement of the rotary compressor 100 is between 13.5 cc and 26 cc, and preferably between 15 cc and 18 cc, but the invention is not limited thereto.

[0038] It should be further noted that the various components of the rotary compressor 100 rotate at different speeds during operation, and the speed difference causes friction between the components. It should also be noted that when the various components of the rotary compressor 100 are operating, reducing the height hc of the cam 31 reduces the frictional contact area between the cam 31 and the inner surface 23 of the ring 2, thereby reducing frictional losses between the cam 31 and the ring 2. Furthermore, reducing the height-to-radius ratio (hr / rr) of the ring 2 reduces the frictional contact area between other components (e.g., pump 1) and the ring 2, thereby reducing frictional losses of the ring 2. And, reducing the minimum radius rs of the shaft 3 reduces the frictional contact area between other components (e.g., pump 1) and the shaft 3, thus reducing frictional losses.

[0039] Accordingly, the rotary compressor 100 provided in this embodiment can significantly reduce frictional losses between the various components of the rotary compressor 100 by designing the height-to-radius ratio (hr / rr) of the ring 2, the minimum radius rs of the shaft 3, and the height hc of the cam 31, thereby effectively improving the operating efficiency of the rotary compressor 100 (i.e., improving refrigeration efficiency). In other words, the various components of the rotary compressor 100 can maintain low frictional losses during operation.

[0040] It is worth mentioning that the shaft 3 is a hollow cylinder, so that an oil pump (not shown) can be further connected to the shaft 3. Specifically, the oil pump can be used to supply an oil body, and the oil body can be supplied to the rotary compressor 100 through the shaft 3.

[0041] Furthermore, the oil preferably has a volume between 150 cc and 270 cc, and the oil provides lubrication for the various components of the rotary compressor 100 during operation, further reducing frictional losses during operation. More specifically, the oil is selected from one of a PAG type oil (i.e., polyethylene glycol synthetic oil) and a POE type oil (i.e., polyol ester). Further, the PAG type oil has a kinematic viscosity between 90 cSt and 110 cSt at a temperature of 40°C, and the POE type oil has a kinematic viscosity between 62 cSt and 74 cSt at a temperature of 40°C.

[0042] Re-reference Figure 2 As shown, the blade 4 extends from the outside of the pump 1 into the chamber A, and the blade 4 can contact the outer surface 22 of the ring 2. Specifically, as the ring 2 rotates, the blade 4 can slide in and out of the chamber A to draw in gas and contact the outer surface 22 of the ring 2, forming sealed spaces of different sizes in the chamber A, thereby effectively compressing the gas.

[0043] The components and their arrangement in the rotary compressor 100 have been described above. Based on the above configuration, the rotary compressor 100 provided in this embodiment can complete cooling in less than 90 seconds, and preferably, the time is no more than 70 seconds.

[0044] In practice, when the rapid freezing appliance 201 (e.g., an ice cream machine) uses the rotary compressor 100, it only takes about 60 seconds to complete the cooling process. However, when the rapid freezing appliance 201 (e.g., an ice cream machine) uses a reciprocating compressor, the reciprocating compressor takes about 120 seconds to complete the cooling process. Therefore, the rotary compressor 100 provided in this embodiment does indeed have a better rapid cooling effect compared to the reciprocating compressor.

[0045] In summary, the rotary compressor for rapid freezing appliances disclosed in the embodiments of the present invention can achieve this by selecting specific refrigerants such as R1270 or R290, and by having a discharge port with a diameter of 28 square millimeters (mm²). 2 The design of the effective area of ​​51 square millimeters reduces the pressure drop when the refrigerant of R1270 or R290 passes through the valve (e.g., a flow restrictor), thereby effectively improving the operating efficiency of the rotary compressor and simultaneously improving the refrigeration efficiency.

[0046] The above-disclosed content is only a preferred and feasible embodiment of the present invention and is not intended to limit the patent scope of the present invention. Therefore, all equivalent technical changes made using the contents of the present invention specification and drawings are included within the patent scope of the present invention.

Claims

1. A rotary compressor for use in rapid refrigeration appliances, wherein the rotary compressor is capable of charging a refrigerant selected from R1270 and R290; characterized in that, The rotary compressor includes: A pump having a first longitudinal axis, the pump comprising: An upper support has a discharge outlet having a depth of no more than 2 mm and an effective area between 28 square millimeters and 51 square millimeters; wherein the discharge outlet is capable of discharging the refrigerant. A cylinder body, connected to the upper support, the cylinder body having a suction port, and the suction port being capable of drawing in the refrigerant; and A lower support is located on the side away from the upper support, and the upper support, the cylinder body, and the lower support together form a chamber; A ring having a second longitudinal axis parallel to and spaced from the first longitudinal axis, and the ring being disposed within the pump; wherein the ring has a height-to-radius ratio between 1.4 and 1.7; A shaft, passing along the first longitudinal axis and contacting the ring; the shaft is rotatable relative to the first longitudinal axis, so that the ring is rotatable relative to the pump; and A blade extends from the outside of the pump into the chamber, and the blade can contact an outer side of the ring.

2. The rotary compressor for rapid freezing appliances as described in claim 1, characterized in that, The shaft further includes a cam located within the cavity, and the cam is capable of contacting an inner side surface of the ring; the cam has a height not exceeding 24 mm.

3. The rotary compressor for rapid freezing appliances as described in claim 2, characterized in that, The height of the cam is between 10 mm and 16 mm.

4. The rotary compressor for rapid freezing appliances as described in claim 3, characterized in that, The portion of the shaft excluding the cam has a minimum radius of no more than 9 mm relative to the first longitudinal axis.

5. The rotary compressor for rapid freezing appliances as described in claim 1, characterized in that, The displacement of the rotary compressor is between 13.5 cc and 26 cc.

6. The rotary compressor for rapid freezing appliances as described in claim 5, characterized in that, The displacement of the rotary compressor is between 15 cc and 18 cc.

7. The rotary compressor for rapid freezing appliances as described in claim 1, characterized in that, The rotary compressor further includes an oil body selected from a PAG type oil and a POE type oil; the PAG type oil has a kinematic viscosity between 90 cSt and 110 cSt at a temperature of 40°C, and the POE type oil has a kinematic viscosity between 62 cSt and 74 cSt at a temperature of 40°C.

8. The rotary compressor for rapid freezing appliances as described in claim 7, characterized in that, The oil volume is between 150 cc and 270 cc.

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