Rotating machinery

Abstract

The present application provides a kind of rotating machinery, which includes rotating shaft, oil supply passage is arranged in rotating shaft and extends substantially along the axial direction of rotating shaft, and the rotating machinery further includes oil supply control device, which includes: oil drain hole, oil drain hole is formed in rotating shaft and communicates oil supply passage with the outside of rotating shaft;And oil drain valve, oil drain valve includes valve piece, wherein, the oil supply control device further includes control piece, control piece is movably retained to rotating shaft, so that the movement of control piece can cause valve piece to move between the opening position of opening oil drain hole and the closed position of closing oil drain hole.The rotating machinery according to the present application can realize balanced oil supply in full speed range, stable and reliable performance, simple manufacturing and maintenance.

Description

Technical Field

[0001] The present invention relates to an oil supply control device and rotating machinery having the oil supply control device, and more specifically, to an oil supply control device suitable for a variable frequency compressor and a variable frequency compressor having the oil supply control device. Background Technology

[0002] This section provides background information related to the present invention, which does not necessarily constitute prior art.

[0003] In this document, rotating machinery refers to mechanical equipment or systems having a rotating shaft, crankshaft, or rotating drive shaft, such as a scroll compressor. A scroll compressor includes a compression mechanism for compressing a working fluid and a rotating shaft for driving the compression mechanism. Typically, during compressor operation, the rotating shaft rotates to drive the compression mechanism to compress the working fluid, while lubricant is supplied through internal through-holes in the rotating shaft to the various moving parts of the compressor (including bearings, bushings, scrolls, etc.) or thrust surfaces. For example, lubricant (e.g., lubricating oil) needs to be supplied between the moving scroll component and the stationary scroll component of the compression mechanism to improve friction between them, thereby reducing wear and power consumption.

[0004] In existing variable frequency compressors, the lubricating oil supplied to the compression mechanism mainly comes from the following two aspects: one is the lubricating oil carried by the working fluid sucked into the scroll compression chamber, and the other is the lubricating oil that enters the scroll compression chamber through the internal through hole of the rotating shaft via the moving scroll oil supply channel.

[0005] While this oil circuit design ensures oil supply at low compressor speeds, the rapid increase in oil supply from the internal through-holes of the rotating shaft during high-speed operation leads to excessive oil intake into the scroll compressor chamber. This affects the heat exchange efficiency of the compressor and system, reducing the compressor's energy efficiency. Simultaneously, an excessively high oil recirculation rate (ORC) will also cause a decrease in the oil level in the compressor's oil sump, impacting compressor reliability.

[0006] Therefore, the present invention aims to provide an oil supply control device that satisfies the oil supply balance of the compressor across the entire speed range. Summary of the Invention

[0007] This section provides a general overview of the invention, rather than a full disclosure of the invention's complete scope or all its features.

[0008] One of the objectives of this invention is to provide an oil supply control device that can balance the lubricating oil supply of a compressor, especially an oil supply control device that prevents excessive oil supply to the compressor under high-speed conditions.

[0009] Another object of the present invention is to provide a rotating machine, particularly a variable frequency compressor, which can achieve balanced oil supply across the entire speed range, avoiding energy efficiency reduction or even failure caused by excessively high oil circulation rate.

[0010] Another objective of this invention is to provide an oil supply control device and a rotating machine that are modular, easy to manufacture, easy to replace and maintain, and inexpensive.

[0011] The present invention provides a rotating machine including a rotating shaft, wherein an oil supply channel is provided within the rotating shaft extending generally along the axial direction of the rotating shaft, and the rotating machine further includes an oil supply control device comprising: an oil drain hole formed in the rotating shaft and communicating the oil supply channel with the outside of the rotating shaft; and an oil drain valve including a valve plate, wherein the oil supply control device further includes a control member movably held on the rotating shaft such that movement of the control member causes the valve plate to move between an open position opening the oil drain hole and a closed position closing the oil drain hole.

[0012] Optionally, the control element is a control pin.

[0013] Optionally, the control pin is held in the drain hole, and there is a channel between the control pin and the wall of the drain hole and / or a hollow channel is formed in the control pin to form a bypass channel for lubricating oil to flow from the oil supply channel to the outside of the rotating shaft.

[0014] Optionally, the drain hole includes a first diameter portion and a second diameter portion arranged from the inside to the outside in the radial direction of the rotating shaft, wherein the inner diameter of the first diameter portion is smaller than the inner diameter of the second diameter portion, and the inner diameter of the first diameter portion is smaller than the outer diameter of the control pin.

[0015] Optionally, the second diameter portion is constructed in the form of a step, including a first flow section located on the radially inner side and a second flow section located on the radially outer side, wherein the cross-sectional area of ​​the first flow section is smaller than the cross-sectional area of ​​the second flow section.

[0016] Optionally, a pin hole is additionally formed on the rotating shaft, the control pin is held in the pin hole, and the valve plate covers both the drain hole and the pin hole in the closed position.

[0017] Optionally, the valve plate includes a main body and a protrusion extending outward from the main body, the main body corresponding to the position of the drain hole and the protrusion corresponding to the position of the pin hole.

[0018] Optionally, the valve plate includes a fixed end fixed to the rotating shaft and a movable end opposite to the fixed end, with the pin hole being farther away from the fixed end than the drain hole.

[0019] Alternatively, the drain hole can be configured as a single hole or multiple holes arranged along the extension direction of the valve plate.

[0020] Optionally, the drain hole is constructed to have a rectangular cross-section, a circular cross-section, or an oblong cross-section. In the case of a rectangular cross-section or an oblong cross-section, the long side of the drain hole is arranged along the extension direction of the valve plate.

[0021] Optionally, the control pin and / or rotating shaft are provided with a stop feature to prevent the control pin from disengaging from the rotating shaft.

[0022] Optionally, the control pin has a non-actuated position located inside the rotating shaft and an actuated position protruding outside the rotating shaft. When the control pin is in the non-actuated position, the valve plate is in the closed position and the valve plate applies preload pressure to the drain hole. When the rotational speed of the rotating shaft exceeds a predetermined value, the control pin moves to the actuated position and overcomes the preload pressure, causing the valve plate to move to the open position.

[0023] Optionally, as the rotational speed of the rotating shaft increases, the degree to which the control pin protrudes beyond the rotating shaft increases, thereby increasing the opening degree of the oil drain hole.

[0024] Optionally, the rotating machinery is a variable frequency scroll compressor.

[0025] In general, the oil supply control device according to the present invention and the rotating machinery using the oil supply control device bring at least the following beneficial effects: when the rotating machinery is running at low speed, it can ensure sufficient oil supply to provide adequate lubrication and cooling, thereby maintaining the performance and reliability of the rotating machinery during low-speed operation; when the rotating machinery is running at high speed, it can prevent excessive oil supply, thereby avoiding a reduction in the energy efficiency and reliability of the rotating machinery; in addition, the oil supply can be adaptively adjusted according to the different operating speeds of the rotating machinery, thereby achieving balanced oil supply across the entire speed range of the rotating machinery; furthermore, the oil supply control device for the rotating machinery is simple to manufacture and process, easy to replace and maintain, and inexpensive. Attached Figure Description

[0026] The foregoing and other features and characteristics of the invention will become clearer from the following detailed description with reference to the accompanying drawings, which are by way of example only and are not necessarily drawn to scale. The same reference numerals are used in the drawings to indicate the same parts, in which:

[0027] Figure 1 A longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention is shown;

[0028] Figure 2 yes Figure 1 A magnified view of detail A in the image;

[0029] Figure 3 An exploded view of the oil supply control device and the rotating shaft according to a first embodiment of the present invention is shown;

[0030] Figure 4 It shows Figure 3 A magnified view of detail B in the image;

[0031] Figure 5 An exploded view of the oil supply control device and the rotating shaft according to a second embodiment of the present invention is shown;

[0032] Figure 6 It shows Figure 5 A magnified view of detail C in the image; and

[0033] Figure 7 A longitudinal sectional view of the oil supply control device and the rotating shaft according to a second embodiment of the present invention is shown. Detailed Implementation

[0034] Now we will combine Figures 1 to 7 Preferred embodiments of the invention will be described in detail below. In the various views, corresponding components or portions are given the same reference numerals. The following description is exemplary in nature and is not intended to limit the invention or its application or use. In the drawings, rotating machinery is shown as a variable frequency scroll compressor; however, those skilled in the art will understand that the oil supply control device according to the invention is applicable to any other suitable type of mechanical equipment or system having a rotating shaft, crankshaft, or rotating rotating shaft.

[0035] First, refer to Figure 1 The overall structure and operating principle of the scroll compressor according to the present invention are described.

[0036] like Figure 1 As shown, the variable frequency scroll compressor 100 (hereinafter sometimes referred to as a scroll compressor or compressor) generally includes a housing 10, a compression mechanism consisting of a fixed scroll component 20 and a moving scroll component 30, a main bearing housing 40, and a rotating shaft 50 and a motor 60 for driving the compression mechanism. The helical blades of the moving scroll component 30 mesh with the helical blades of the fixed scroll component 20 to form a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side. An eccentric crank pin is provided at one end of the rotating shaft 50 adjacent to the moving scroll component 30. The eccentric crank pin is inserted into the hub of the moving scroll component 30. Driven by the motor 60, the rotating shaft 50 causes the moving scroll component 30 to rotate relative to the fixed scroll component 20 via the eccentric crank pin, thereby compressing the working fluid.

[0037] Lubricant (e.g., lubricating oil) is needed for lubrication and cooling between the moving parts of the scroll compressor 100, such as between the helical blades of the moving scroll component 30 and the helical blades of the stationary scroll component 20. Figure 1In the scroll compressor shown, a sump for storing lubricating oil is formed at the bottom of the housing 10. Correspondingly, an oil supply channel extending substantially axially is formed in the rotating shaft 50. This oil supply channel may include a central channel 51 formed at the lower end of the rotating shaft 50 and an eccentric channel 52 extending upward from the central channel 51 to the end face of the eccentric crankpin. During compressor operation, lubricating oil in the sump is supplied to the central channel 51 at the lower end of the rotating shaft 50. The lubricating oil entering the central channel 51 is pumped or thrown into the eccentric channel 52 by centrifugal force during the rotation of the rotating shaft 50 and flows upward along the eccentric channel 52 until it reaches the end face of the eccentric crankpin. Part of the lubricating oil discharged from the end face of the eccentric crankpin is used to lubricate the eccentric crankpin and the components near the moving scroll hub, and is subsequently discharged from the main bearing housing 40 and returned to the sump. Another part is pushed into the moving scroll oil passage 32, which communicates with the compression chamber, in the end plate of the moving scroll component 30. Therefore, lubricating oil can enter the compression chamber through two pathways: firstly, it can enter the compression chamber via the oil supply channel and the moving scroll oil passage 32; secondly, small oil droplets formed during the lubrication of other components (such as the thrust surface of the main bearing housing 40) can be drawn into the compression chamber along with the working fluid. These two pathways ensure a sufficient supply of lubricating oil in the compression chamber, thereby guaranteeing adequate lubrication between the moving scroll component 30 and the stationary scroll component 20, and especially avoiding the problem of insufficient oil supply and easy malfunction of the scroll compressor 100 when operating at low speeds.

[0038] However, when the scroll compressor 100 operates at high speed, the amount of oil supplied to the oil supply passage within the rotating shaft 50 increases rapidly, and the amount of oil entering the compression chamber via the moving scroll oil passage 32 also increases rapidly. This can easily lead to an excessively high oil circulation rate in the compressor, affecting the compressor and system energy efficiency. Therefore, an oil supply control device is also installed on the rotating shaft 50, such as... Figure 1 Detail A is shown in the image.

[0039] See Figure 2 and Figure 3 The oil supply control device is installed in the mounting area S of the rotating shaft 50, such as... Figure 3As shown in detail B. Within the mounting area S, the outer surface of the rotating shaft 50 is formed as a plane that is slightly concave relative to the arcuate surfaces of other areas, thereby preventing the oil supply control device from protruding excessively from the outer surface of the rotating shaft 50 and affecting other parts of the compressor, and making it easier to operate and install the control valve. The oil supply control device includes an oil drain hole 53a formed in the rotating shaft 50, a control valve 70a fixed to the rotating shaft 50, and a control element movably held on the rotating shaft 50. In the first embodiment of the invention, the control element is implemented as a control pin 74a, but those skilled in the art will understand that the control element can also be implemented in any other suitable form, such as a ball. The oil drain hole 53a communicates the central channel 51 with the outer space of the rotating shaft 50. Preferably, the oil drain hole 53a is configured to extend generally radially along the rotating shaft 50 so that lubricating oil can be discharged from the central channel 51 under the action of centrifugal force. In some other examples, the drain hole can also be configured to connect the eccentric channel 52 to the outer space of the rotating shaft 50, and positioned relative to the central axis of the eccentric channel 52 on the opposite side to the central axis of the rotating shaft 50, thereby facilitating the discharge of a portion of the lubricating oil in the eccentric oil passage 52 to the outside of the rotating shaft under centrifugal force. The rotating shaft 50 also has a mounting hole 55 (blind hole) above the drain hole 53a and a pin hole 56a (blind hole) below the drain hole 53a. The mounting hole 55 is used to fix the control valve 70a, while the pin hole 56a is used to accommodate the control pin 74a. The cross-sectional shape of the pin hole 56a is substantially the same as that of the control pin 74a, but the cross-sectional size of the pin hole 56a is slightly larger than that of the control pin 74a, allowing the sliding of the control pin 74a to be guided by the hole wall of the pin hole 56a, thus making the sliding of the control pin 74a smoother.

[0040] See Figure 4 The control valve 70a is constructed as a reed valve, including a valve plate 73a, a valve cover 71a, and a fastener 72a (e.g., a screw). The valve cover 71a is disposed outside the valve plate 73a and corresponds to the shape of the valve plate 73a to protect the valve plate 73a. The valve plate 73a includes a fixed end 731a and a movable end 732a, with a through hole formed at its fixed end 731a. Correspondingly, the valve cover 71a also includes a fixed end 711a, with a through hole formed at its fixed end 711a. The fastener 72a passes sequentially through the through hole at the fixed end 711a of the valve cover 71a and the through hole at the fixed end 731a of the valve plate 73a, and is then inserted into the mounting hole 55 of the rotating shaft 50, thereby detachably securing one end of the control valve 70a to the rotating shaft 50. The valve plate 73a can cover both the drain hole 53a and the pin hole 56a at its movable end 732a.

[0041] The control pin 74a is held in the pin hole 56a and is movable relative to the rotating shaft 50 in approximately the radial direction under the action of centrifugal force. The control pin 74a has a non-actuated position completely within the rotating shaft 50 and an actuated position at least partially protruding outside the rotating shaft 50. When the rotating shaft 50 is stationary or rotating at low speed, the control pin 74a is fully accommodated inside the pin hole 56a in its non-actuated position, at which time the valve plate 73a is in its closed position. The valve plate 73a applies pre-tightening pressure to the drain hole 53a and the pin hole 56a, thereby closing the drain hole 53a. At this time, the control pin 74a and the valve plate 73a are not in contact or are in contact but the force between them is less than the pre-tightening pressure of the valve plate 73a or even zero. As the rotational speed of the rotating shaft 50 increases, the centrifugal force on the control pin 74a increases. When the rotational speed of the rotating shaft 50 exceeds a predetermined value, the centrifugal force on the control pin 74a is greater than the preload pressure of the valve plate 73a. The control pin 74a overcomes the preload pressure of the valve plate 73a and moves towards the outside of the rotating shaft 50 to its actuated position. At the actuated position, the control pin 74a pushes up the valve plate 73a, causing the valve plate 73a to move from its closed position to its open position. The valve plate 73a leaves (or at least partially leaves) the drain hole 53a, thereby allowing a portion of the lubricating oil in the oil supply channel to be discharged through the drain hole 53a to the outside of the rotating shaft 50 and return to the oil sump.

[0042] Those skilled in the art will understand that as the rotational speed of the rotating shaft 50 increases, the amount of oil entering the oil supply channel within the rotating shaft 50 also increases, thus posing a risk of excessive oil supply. However, simultaneously, the degree to which the control pin 74a protrudes beyond the rotating shaft 50 also increases, and the opening degree of the oil drain hole 53a increases accordingly, allowing more lubricating oil in the oil supply channel to be discharged outside the rotating shaft 50, thereby effectively preventing a large amount of lubricating oil from entering the compression chamber. Therefore, the oil supply control device according to the present invention can adapt to the rotational speed of the rotating shaft 50, preventing excessively high oil circulation rates in the compressor and achieving balanced oil supply across the entire speed range. Furthermore, by employing a control pin independent of the control valve to actuate the opening and closing of the control valve, the control pin can be manufactured and installed independently, resulting in a simple structure, convenient manufacturing and installation, and easy adjustment and maintenance. Moreover, the separate design of the pressure relief hole and the pin hole allows for individual processing of the pressure relief hole and the pin hole, resulting in flexible design, simple process, and low cost.

[0043] Preferably, the control pin 74a and / or the pin hole 56a of the rotating shaft 50 are provided with a stop feature, for example, a flange is formed on the outer peripheral wall of the control pin 74a and a protrusion is formed on the inner wall of the pin hole 56a to cooperate with the flange of the control pin 74a, thereby limiting the distance that the control pin 74a protrudes beyond the rotating shaft 50 and preventing the control pin 74a from disengaging from the rotating shaft 50 under extreme working conditions.

[0044] Preferably, the movable end 732a of the valve plate 73a has a main body 733a corresponding to the position of the drain hole 53a and a protrusion 734a extending outward from the main body 733a corresponding to the position of the pin hole 56a. The control pin 74a opens the drain hole 53a by lifting the protrusion 734a, thereby disengaging the main body 733a from the drain hole 53a. This design makes it easier for the control pin to lift the valve plate and allows for more space for the arrangement of the pressure relief hole and the pin hole as needed, making the shape and size design of the pressure relief hole more flexible.

[0045] Furthermore, although the mounting hole 55 and pin hole 56a are shown in the figure as being located on the upper and lower sides of the drain hole 53a respectively, those skilled in the art will understand that the mounting hole and pin hole can also be located on the left and right sides of the drain hole 53a respectively, or even on one side of the drain hole 53a, as long as the mounting hole, pin hole, and drain hole 53a are arranged along the extension direction of the valve plate. In this document, the extension direction of the valve plate refers to the direction in which the valve plate extends between its fixed end and movable end, and is not limited to the axial direction along the rotation axis shown in the embodiments of the present invention. However, preferably, the pin hole is further away from the fixed end of the valve plate than the drain hole 53a, thereby making it easier to lift the valve plate. In addition, the valve plate preferably extends along the axial direction of the rotation axis, with the fixed end located above the drain hole and the pin hole located below the drain hole, thereby making it easier for the lubricating oil to be discharged from the drain hole under the action of centrifugal force and for the discharged lubricating oil to flow back to the oil sump more easily.

[0046] Figures 5 to 7 A second embodiment of the present invention is shown. In the second embodiment of the present invention, the overall structure and operating principle of the compressor are basically the same as those of the first embodiment of the present invention, and will not be described again here. Unlike the first embodiment of the present invention, in the oil supply control device of the second embodiment of the present invention, the control pin is not housed in a separate pin hole, but is directly held in the oil drain hole.

[0047] See Figure 5 and Figure 6 The control device is kept in the mounting area S of the rotating shaft 50, such as... Figure 5 As shown in detail C, the oil supply control device includes an oil drain hole 53b formed in the rotating shaft 50, a control valve 70b fixed to the rotating shaft 50, and a control pin 74b movably held on the rotating shaft 50. The oil drain hole 53b is configured to extend generally radially along the rotating shaft 50 and communicate with the outer space of the rotating shaft 50 through the central channel 51. A mounting hole 55 (blind hole) is also formed in the rotating shaft 50 above the oil drain hole 53b, wherein the mounting hole 55 is used to fix the control valve 70b, and the control pin 74b is directly received in the oil drain hole 53b.

[0048] See Figure 6 The control valve 70b is constructed as a reed valve, including a valve plate 73b, a valve cover 71b, and a fastener 72b (e.g., a screw). The valve cover 71b is disposed outside the valve plate 73b and corresponds to the shape of the valve plate 73b to protect the valve plate 73b. The valve plate 73b includes a fixed end 731b and a movable end 732b, with a through hole formed at its fixed end 731b. Correspondingly, the valve cover 71b also includes a fixed end 711b, with a through hole formed at its fixed end 711b. The fastener 72b passes sequentially through the through holes at the fixed end 711b of the valve cover 71b and the fixed end 731b of the valve plate 73b, and is then inserted into the mounting hole 55 of the rotating shaft 50, thereby detachably securing one end of the control valve 70b to the rotating shaft 50. The valve plate 73b can cover the drain hole 53b at its movable end 732b.

[0049] The control pin 74b is held in the drain hole 53b and is movable relative to the rotating shaft 50 in approximately the radial direction under centrifugal force. To form a bypass channel for lubricating oil to flow from the central channel 51 to the outside of the rotating shaft 50, a groove exists between the control pin 74b and the wall of the drain hole 53b; that is, the groove can be formed on the wall of the drain hole (e.g., ...). Figure 7 The channel 534b (shown in the figure) formed on the inner wall of the drain hole 53b can be formed on the outer peripheral wall of the control pin, or on both the hole wall of the drain hole and the outer peripheral wall of the control pin. Alternatively or additionally, a hollow channel (not shown) can also be formed within the control pin 74b as a bypass channel for lubricating oil. The inlet end of this hollow channel communicates with the central channel 51, and the outlet end of this hollow channel is preferably located at a position that communicates with the outside of the rotating shaft 50 but does not contact the valve plate 73b, thereby preventing the outlet end of the hollow channel from being blocked by the valve plate 73b when the control pin 74b lifts the valve plate 73b, thus affecting the smooth discharge of lubricating oil. For example, the hollow channel includes a transverse section and a longitudinal section connected to each other. The transverse section is connected to the central channel 51, while the longitudinal section is connected to the outside of the rotating shaft 50. The outlet of the longitudinal section (i.e. the outlet of the central channel) is formed on the outer peripheral wall of the control pin 74b near its radially outer end. Thus, the lubricating oil in the central channel 51 is not affected by the valve plate 73b when it is discharged through the hollow channel.

[0050] See Figure 7The drain hole 53b includes a first diameter portion 531b and a second diameter portion arranged radially from the inside to the outside in the rotational shaft 50. The inner diameter of the first diameter portion 531b is smaller than the inner diameter of the second diameter portion, and the inner diameter of the first diameter portion 531b is smaller than the outer diameter of the control pin 74b. Thus, when the control pin 531b is installed in the drain hole 53b, the control pin 531b is accommodated in the second diameter portion, and the radially inner end of the control pin 531b abuts against the step portion formed between the first diameter portion 531b and the second diameter portion, thereby preventing the control pin 531b from disengaging from the rotational shaft 50 and entering the central channel 51.

[0051] The second diameter section can be constructed as a smooth straight hole or as a stepped shape as shown in the figure. For example... Figure 7 As shown, the second diameter portion includes a first flow section 532b located radially inner and a second flow section 533b located radially outer. The cross-sectional area of ​​the first flow section 532b is smaller than that of the second flow section 533b, thereby achieving a progressively increasing oil discharge volume, achieving the goal of greater oil discharge volume with higher rotational speed. For example, the cross-section of the first flow section is circular, while the cross-section of the second flow section is elliptical or oblong, wherein the minor axis of the cross-section of the second flow section is equal to the diameter of the cross-section of the first flow section, so that the control pin is held and guided by the bore wall on both sides in the minor axis direction within the second flow section. Alternatively, the cross-sections of both the first and second flow sections are circular, and multiple (e.g., three or four) ridges are formed on the bore wall of the second flow section, distributed circumferentially along the second flow section, to hold and guide the control pin within the second flow section.

[0052] When the second diameter portion is constructed in a stepped form, the control pin 74b has a non-actuated position completely within the rotating shaft 50, a first actuated position partially protruding outside the rotating shaft 50, and a second actuated position protruding further outside the rotating shaft 50 than the first actuated position. When the rotating shaft 50 is stationary or rotating at low speed, the control pin 74b is completely accommodated inside the drain hole 53b and is in its non-actuated position. At this time, the valve plate 73b is in its closed position, and the valve plate 73b applies pre-tightening pressure to the drain hole 53b, thereby closing the drain hole 53b. At this time, the control pin 74b and the valve plate 73b are not in contact or are in contact but the force between them is less than the pre-tightening pressure of the valve plate 73b or even zero. As the rotational speed of the rotating shaft 50 increases, the centrifugal force on the control pin 74b increases. When the rotational speed of the rotating shaft 50 exceeds a predetermined value, the centrifugal force on the control pin 74b is greater than the preload pressure of the valve plate 73b. The control pin 74b overcomes the preload pressure of the valve plate 73b and moves outward toward the first actuated position of the rotating shaft 50. At the first actuated position, the control pin 74b lifts the valve plate 73b, opening the oil drain hole 53b. At this time, the flow area of ​​lubricating oil discharged through the oil drain hole 53b is the flow area within the first flow section 532b (for example, the flow area formed by a channel between the control pin 74b and the wall of the oil drain hole 53b, and / or by a hollow channel formed within the control pin 74b). When the rotational speed of the rotating shaft 50 further increases, the control pin 74b moves further outward to its second actuated position, exposing the second flow section 533b. At this time, the flow area of ​​lubricating oil discharged through the oil drain hole 53b is the flow area within the second flow section 532b. Because the cross-sectional area of ​​the second flow section 533b is larger than that of the first flow section 532b, the flow area within the second flow section 532b includes not only the flow area formed by, for example, the channel between the control pin 74b and the wall of the drain hole 53b and / or the hollow channel formed within the control pin 74b, but also the flow area formed by the increased gap between the control pin 74b and the inner wall of the drain hole 53b (this increased gap, for example, refers to the gap between the control pin and the wall of the drain hole in the long axis direction of the elliptical / oblong second flow section). Simultaneously, as the degree to which the control pin 74b protrudes beyond the rotating shaft 50 increases, the opening degree of the drain hole 53b increases accordingly. Therefore, in its second actuated position, the control pin 74b allows more lubricating oil in the oil supply channel to be discharged outside the rotating shaft 50 compared to its first actuated position.

[0053] Therefore, the oil supply control device according to the present invention can adapt to the rotational speed of the rotating shaft 50, preventing the oil circulation rate of the compressor from being too high and achieving balanced oil supply across the entire speed range. Furthermore, since the control pin is directly disposed in the pressure relief hole, the design of the pin hole is omitted, simplifying processing and installation.

[0054] The accompanying drawings illustrate only two exemplary embodiments within the framework of this invention. Those skilled in the art will understand that this invention is not limited to the exemplary embodiments described above, but also includes variations or combinations of the various examples described above. For example, the drain hole can be a single hole or more than one hole. Furthermore, the pressure relief hole can be constructed in various shapes as needed, such as a circular, oblong, rectangular, or other suitable cross-section. Preferably, drain holes constructed as multiple holes are arranged along the extension direction of the valve plate, and / or drain holes constructed as oblong or rectangular have their long sides arranged along the extension direction of the valve plate, such that as the degree to which the valve plate is lifted by the control pin increases, the opening degree of the drain hole gradually increases, thereby achieving the purpose of increasing the oil discharge volume of the drain hole as the rotational speed of the shaft increases.

[0055] The rotating machinery according to a preferred embodiment of the present invention has been described above with reference to specific embodiments. It is understood that the above description is exemplary and not restrictive, and various modifications and variations can be conceived by those skilled in the art with reference to the above description without departing from the scope of the invention. These modifications and variations are also included within the scope of protection of the present invention.

Claims

1. A rotating machine, the rotating machine comprising a rotating shaft (50), wherein the rotating shaft has an oil supply channel extending substantially along the axial direction of the rotating shaft, the rotating machine further comprising an oil supply control device (70a, 70b), the oil supply control device comprising: Oil drain holes (53a, 53b), said oil drain holes being formed in the rotating shaft and communicating the oil supply channel with the outside of the rotating shaft; and Oil drain valves (70a, 70b), wherein the oil drain valves include valve plates (73a, 73b). The oil supply control device is characterized in that it further includes a control element, which is movably held on the rotating shaft, such that the movement of the control element causes the valve plate to move between an open position that opens the oil drain hole and a closed position that closes the oil drain hole.

2. The rotating machinery according to claim 1, wherein, The control components are control pins (74a, 74b).

3. The rotating machinery according to claim 2, wherein, The control pin (74b) is held in the drain hole (53b), and there is a channel (534b) between the control pin and the wall of the drain hole and / or a hollow channel is formed in the control pin to form a bypass channel for lubricating oil to flow from the oil supply channel to the outside of the rotating shaft.

4. The rotating machinery according to claim 3, wherein, The drain hole includes a first diameter portion (531b) and a second diameter portion arranged from the inside to the outside in the radial direction of the rotating shaft. The inner diameter of the first diameter portion is smaller than the inner diameter of the second diameter portion, and the inner diameter of the first diameter portion is smaller than the outer diameter of the control pin.

5. The rotating machinery according to claim 4, wherein, The second diameter portion is constructed in a stepped form, including a first flow section (532b) located on the radially inner side and a second flow section (533b) located on the radially outer side, wherein the cross-sectional area of ​​the first flow section is smaller than the cross-sectional area of ​​the second flow section.

6. The rotating machinery according to claim 2, wherein, A pin hole (56a) is additionally formed on the rotating shaft, the control pin (74a) is held in the pin hole, and the valve plate covers both the drain hole and the pin hole in the closed position.

7. The rotating machinery according to claim 6, wherein, The valve plate includes a main body (733a) and a protrusion (734a) extending outward from the main body. The main body corresponds to the position of the drain hole, and the protrusion corresponds to the position of the pin hole.

8. The rotating machinery according to claim 6, wherein, The valve plate includes a fixed end (731a) fixed to the rotating shaft and a movable end (732a) opposite to the fixed end, and the pin hole is further away from the fixed end than the drain hole.

9. The rotating machinery according to any one of claims 1 to 8, wherein, The drain hole can be a single hole or multiple holes arranged along the extension direction of the valve plate.

10. The rotating machinery according to any one of claims 1 to 8, wherein, The drain hole is constructed to have a rectangular cross-section, a circular cross-section, or an oblong cross-section. In the case of a rectangular or oblong cross-section, the long side of the drain hole is arranged along the extension direction of the valve plate.

11. The rotating machinery according to any one of claims 1 to 8, wherein, The control element and / or the rotating shaft are provided with a stop feature to prevent the control element from disengaging from the rotating shaft.

12. The rotating machinery according to any one of claims 1 to 8, wherein, The control element has a non-actuated position located within the rotating shaft and an actuated position protruding outside the rotating shaft. When the control element is in the non-actuated position, the valve plate is in the closed position and the valve plate applies preload pressure to the drain hole. When the rotational speed of the rotating shaft exceeds a predetermined value, the control element moves to the actuated position and overcomes the preload pressure, causing the valve plate to move to the open position.

13. The rotating machinery according to claim 12, wherein, As the rotational speed of the rotating shaft increases, the extent to which the control component protrudes beyond the rotating shaft also increases, thereby increasing the opening degree of the oil drain hole.

14. The rotating machinery according to any one of claims 1 to 8, wherein, The rotating machinery is a variable frequency scroll compressor (100).

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