CN117167281A - Rotary machine - Google Patents

Abstract

The present invention provides a rotary machine including a rotary shaft in which an oil supply passage extending substantially in an axial direction of the rotary shaft is provided, the rotary machine further including an oil supply control device including: an oil drain hole formed in the rotation shaft and communicating the oil supply passage with an outside of the rotation shaft; and an oil drain valve including a valve sheet, wherein the oil supply control device further includes a control member movably held to the rotation shaft such that movement of the control member can cause the valve sheet to move between an open position to open the oil drain hole and a closed position to close the oil drain hole. According to the rotary machine, balanced oil supply in a full rotating speed range can be realized, the performance is stable and reliable, and the manufacture and the maintenance are simple.

Description

Rotary machine

Technical Field

The present invention relates to an oil supply control device and a rotary machine having the same, and more particularly, to an oil supply control device suitable for a variable frequency compressor and a variable frequency compressor having the same.

Background

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

In this context, a rotating machine refers to a mechanical device or system having a rotating shaft, crankshaft, or rotating drive shaft, such as a scroll compressor. The scroll compressor includes a compression mechanism for compressing a working fluid and a rotation shaft for driving the compression mechanism. Generally, when the compressor is operated, the rotary shaft rotates to drive the compression mechanism to compress the working fluid, while lubricant is supplied to each moving part (including bearings, bushings, scrolls, etc.) or thrust surfaces of the compressor via the inner through-hole of the rotary shaft. For example, it is necessary to supply a lubricant (e.g., lubricating oil) between an orbiting scroll member and a non-orbiting scroll member of a compression mechanism to improve friction between the orbiting scroll member and the non-orbiting scroll member, thereby reducing wear and power consumption.

In the existing inverter compressors, the lubrication oil supplied to the compression mechanism is mainly derived from the lubrication oil carried by the working fluid sucked into the scroll compression chambers on the one hand, and from the lubrication oil introduced into the scroll compression chambers through the orbiting scroll oil supply passage through the inner through hole of the rotary shaft on the other hand.

The oil circuit design can ensure the oil supply of the compressor under the condition of low speed, but under the condition of high-speed operation of the compressor, the oil supply from the internal through hole of the rotating shaft is rapidly increased, so that excessive oil is sucked into the vortex compression cavity, the heat exchange efficiency of the compressor and the system is influenced, and the energy efficiency of the compressor is reduced. At the same time, too high an oil circulation rate (ORC) will also lead to a decrease in the oil sump level within the compressor, affecting the reliability of the compressor.

Accordingly, it is desirable to provide an oil supply control apparatus that satisfies oil supply balance of a compressor in a full rotation speed range.

Disclosure of Invention

The accompanying drawings are included to provide a general overview of the invention and are not intended to provide a complete disclosure of the full scope of the invention or all-character thereof.

An object of the present invention is to provide an oil supply control device capable of balancing the supply amount of lubricating oil to a compressor, particularly an oil supply control device capable of avoiding excessive oil supply to the compressor under the condition of high rotation speed of the compressor.

Another object of the present invention is to provide a rotary machine, in particular a variable frequency compressor, which is capable of achieving an even oil supply in the full rotation speed range, avoiding the reduction of energy efficiency and even failure caused by an excessively high oil circulation rate.

Another object of the present invention is to provide an oil supply control device and a rotary machine that are manufactured separately, are easy to manufacture, are easy to replace and repair, and are inexpensive.

The present invention provides a rotary machine including a rotary shaft in which an oil supply passage extending substantially in an axial direction of the rotary shaft is provided, the rotary machine further including an oil supply control device including: an oil drain hole formed in the rotation shaft and communicating the oil supply passage with an outside of the rotation shaft; and an oil drain valve including a valve sheet, wherein the oil supply control device further includes a control member movably held to the rotation shaft such that movement of the control member can cause the valve sheet to move between an open position to open the oil drain hole and a closed position to close the oil drain hole.

Optionally, the control member is a control pin.

Optionally, the control pin is held in the drain hole with a channel between the control pin and a wall of the drain hole and/or a hollow duct is formed in the control pin to constitute a bypass passage for outflow of lubricating oil from the oil supply passage to an outside of the rotary shaft.

Alternatively, the drain hole includes a first diameter portion and a second diameter portion arranged from inside to outside in a radial direction of the rotary shaft, an inner diameter of the first diameter portion is smaller than an inner diameter of the second diameter portion, and an inner diameter of the first diameter portion is smaller than an outer diameter of the control pin.

Optionally, the second diameter portion is configured in a stepped form including a first flow-through section located radially inward and a second flow-through section located radially outward, the cross-sectional area of the first flow-through section being smaller than the cross-sectional area of the second flow-through section.

Optionally, a pin hole is additionally formed on the rotation shaft, the control pin is held in the pin hole, and the valve plate covers both the oil drain hole and the pin hole in the closed position.

Optionally, the valve plate includes a main body portion and a protruding portion extending outward from the main body portion, the main body portion corresponds to a position of the oil drain hole, and the protruding portion corresponds to a position of the pin hole.

Optionally, the valve plate includes a fixed end fixed to the rotation shaft and a movable end opposite to the fixed end, and the pin hole is further away from the fixed end than the drain hole.

Alternatively, the oil drain hole is configured as a single hole or as a plurality of holes arranged along the extending direction of the valve plate.

Alternatively, the drain hole is configured to have a rectangular cross section, a circular cross section, or an oblong cross section, in which case the long edge of the drain hole is arranged along the extending direction of the valve plate.

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

Optionally, the control pin has a non-actuated position inside the rotation shaft and an actuated position protruding outside the rotation shaft, in which the valve plate is in a closed position and the valve plate exerts a pre-compression force on the drain hole, in which the control pin moves to the actuated position and the control pin moves the valve plate to the open position against the pre-compression force, in case the rotation speed of the rotation shaft exceeds a predetermined value.

Alternatively, as the rotation speed of the rotation shaft increases, the degree to which the control pin protrudes out of the rotation shaft increases, so that the opening degree of the oil drain hole also increases.

Alternatively the rotary machine is a variable frequency scroll compressor.

In general, the oil supply control device and the rotary machine using the same according to the present invention bring about at least the following advantageous effects: when the rotary machine runs at a low speed, enough oil supply can be ensured to provide sufficient lubrication and cooling, so that the performance and the reliability of the rotary machine can be maintained when the rotary machine runs at a low speed, and when the rotary machine runs at a high speed, the oil supply can be prevented from being too high, so that the reduction of the energy efficiency and the reliability of the rotary machine can be avoided; in addition, according to different running speeds of the rotary machine, the oil supply amount can be adaptively adjusted, so that balanced oil supply in the full speed range of the rotary machine is realized; in addition, the oil supply control device of the rotary machine is simple to manufacture and process, easy to replace and maintain and low in cost.

Drawings

The foregoing and additional features and characteristics of the present invention will become more apparent from the following detailed description, taken in conjunction with the accompanying drawings, which are merely exemplary and not necessarily drawn to scale. Like reference numerals are used to designate like parts throughout the accompanying drawings, in which:

fig. 1 shows a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention;

fig. 2 is an enlarged view of detail a in fig. 1;

fig. 3 shows an exploded view of an oil supply control device and a rotary shaft according to a first embodiment of the present invention;

fig. 4 shows an enlarged view of detail B in fig. 3;

fig. 5 shows an exploded view of an oil supply control device and a rotary shaft according to a second embodiment of the present invention;

fig. 6 shows an enlarged view of detail C in fig. 5; and

fig. 7 shows a longitudinal sectional view of an oil supply control device and a rotary shaft according to a second embodiment of the present invention.

Detailed Description

A preferred embodiment of the present invention will now be described in detail with reference to fig. 1 to 7. Corresponding components or parts are denoted by the same reference numerals throughout the various views. The following description is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. In the drawings, the rotary machine is shown as a variable frequency scroll compressor, but it will be appreciated by those skilled in the art that the oil supply control apparatus according to the present invention is applicable to any other suitable type of machine or system having a rotating shaft, crankshaft or rotating shaft.

First, the general construction and operation principle of the scroll compressor according to the present invention will be described with reference to fig. 1.

As shown in fig. 1, a variable frequency scroll compressor 100 (hereinafter sometimes referred to as a scroll compressor or a compressor) generally includes a housing 10, a compression mechanism constituted by a fixed scroll member 20 and an orbiting scroll member 30, a main bearing housing 40, a rotary shaft 50 for driving the compression mechanism, a motor 60, and the like. The spiral vane of the orbiting scroll member 30 and the spiral vane of the non-orbiting scroll member 20 are engaged with each other to form a series of compression chambers therebetween, the volumes of which gradually decrease from the radially outer side to the radially inner side. An end of the rotation shaft 50 adjacent to the orbiting scroll member 30 is provided with an eccentric crank pin. An eccentric crank pin is inserted into the hub of the orbiting scroll member 30. By the driving of the motor 60, the rotation shaft 50 moves the orbiting scroll member 30 with respect to the non-orbiting scroll member 20 via the eccentric crank pin to achieve the compression of the working fluid.

Lubrication and cooling of a lubricant (e.g., lubricating oil) is required between the moving parts of the scroll compressor 100, for example, between the spiral vane of the moving scroll part 30 and the spiral vane of the fixed scroll part 20. In the scroll compressor shown in fig. 1, the bottom of the housing 10 forms an oil sump storing lubricating oil. Accordingly, the rotary shaft 50 has an oil supply passage formed therein extending substantially in the axial direction thereof. The oil supply passage may include a central passage 51 formed at a lower end of the rotation shaft 50 and an eccentric passage 52 extending upward from the central passage 51 to an end surface of the eccentric crank pin. During operation of the compressor, the lubricant in the oil sump is supplied into the central passage 51 at the lower end of the rotation shaft 50, and the lubricant entering the central passage 51 is pumped or thrown into the eccentric passage 52 by centrifugal force during rotation of the rotation shaft 50 and flows up along the eccentric passage 52 up to the end face of the eccentric crankpin. A part of the lubricating oil discharged from the end surface of the eccentric crankpin is used to lubricate the eccentric crankpin and the components near the orbiting scroll hub, and then discharged from the main bearing housing 40 to return to the oil sump, and the other part is pushed into the orbiting scroll oil passage 32 in the end plate of the orbiting scroll member 30 communicating with the compression chamber. Thus, the lubricant can enter the compression chamber from two paths: on the one hand, lubricating oil can enter the compression chambers via the oil supply passage and the orbiting scroll oil passage 32; on the other hand, the lubricating oil is, for example, small oil droplets formed during lubrication of other components (e.g., the thrust surface of the main bearing housing 40) so as to be sucked into the compression chambers with the working fluid. These two approaches ensure that sufficient lubrication is provided in the compression pockets to ensure adequate lubrication between the orbiting scroll member 30 and the non-orbiting scroll member 20, and in particular to avoid the problems of insufficient oil supply and failure in the case of low rotational speed operation of the scroll compressor 100.

However, when the scroll compressor 100 is operated at a high rotational speed, the amount of oil supplied to the oil supply passage in the rotation shaft 50 increases rapidly, and the amount of oil entering the compression chamber through the orbiting scroll passage 32 increases rapidly therewith, which tends to cause an excessively high oil circulation rate of the compressor, affecting the compressor and system energy efficiency. For this purpose, the rotary shaft 50 is also provided with an oil supply control device, as shown in detail a in fig. 1.

Referring to fig. 2 and 3, the oil supply control device is provided in the installation area S of the rotary shaft 50, as shown in detail B in fig. 3. In this installation area S, the outer surface of the rotation shaft 50 is formed as a plane slightly recessed with respect to the arc-shaped surface of the other area, thereby avoiding the oil supply control device from excessively protruding from the outer surface of the rotation shaft 50 to affect other parts of the compressor and facilitating the operation and installation of the control valve. The oil supply control device includes a drain hole 53a formed in the rotary shaft 50, a control valve 70a fixed to the rotary shaft 50, and a control member movably held on the rotary shaft 50. In the first embodiment according to the present invention, the control member is embodied as a control pin 74a, but it will be appreciated by those skilled in the art that the control member may also be embodied in any other suitable form, such as a sphere. The oil drain hole 53a communicates the center passage 51 with the outer space of the rotary shaft 50. Preferably, the drain hole 53a is configured to extend substantially in the radial direction of the rotation shaft 50 so as to facilitate the discharge of the lubricating oil from the central passage 51 under the centrifugal force. In some other examples, the oil drain hole may also be configured to communicate the eccentric passage 52 with the outer space of the rotating shaft 50 and be disposed on the opposite side of the central axis of the rotating shaft 50 with respect to the central axis of the eccentric passage 52, thereby facilitating draining of a portion of the lubricating oil in the eccentric oil passage 52 to the outside of the rotating shaft under the influence of centrifugal force. Also formed in the rotary shaft 50 are a mounting hole 55 (blind hole) located above the oil drain hole 53a and a pin hole 56a (blind hole) located below the oil drain hole 53a, wherein the mounting hole 55 is for fixing the control valve 70a and the pin hole 56a is for accommodating the control pin 74a. The pin hole 56a is substantially identical to the cross-sectional shape of the control pin 74a, and the cross-sectional size of the pin hole 56a is slightly larger than the cross-sectional size of the control pin 74a, so that the sliding of the control pin 74a can be guided by the wall of the pin hole 56a, thereby making the sliding of the control pin 74a smoother.

Referring to fig. 4, the control valve 70a is configured 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 sheet 73a and corresponds to the shape of the valve sheet 73a for protecting the valve sheet 73a. The valve plate 73a includes a fixed end 731a and a movable end 732a, and a through hole is formed at the fixed end 731a thereof. Accordingly, the valve cover 71a also includes a fixed end 711a, at which a through hole is formed at the fixed end 711a thereof. The fastener 72a is inserted into the mounting hole 55 of the rotation shaft 50 after passing 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 sheet 73a in order, thereby detachably fastening one end of the control valve 70a to the rotation shaft 50. The valve plate 73a can cover both the drain hole 53a and the pin hole 56a at the movable end 732a thereof.

The control pin 74a is held in the pin hole 56a and is movable relative to the rotary shaft 50 in a substantially radial direction of the rotary shaft 50 by centrifugal force. The control pin 74a has a non-actuated position entirely within the rotational shaft 50 and an actuated position at least partially protruding out of the rotational shaft 50. In the case where the rotation shaft 50 is stationary or rotates at a low speed, the control pin 74a is completely accommodated inside the pin hole 56a to be in its non-actuated position, and the valve plate 73a is in its closed position, the valve plate 73a applies a pre-tightening pressure to the drain hole 53a and the pin hole 56a, thereby closing the drain hole 53a, and the control pin 74a is not in contact with or in contact with the valve plate 73a but the force between them is smaller than the pre-tightening force of the valve plate 73a even to be zero. As the rotational speed of the rotation shaft 50 increases, the centrifugal force to which the control pin 74a is subjected increases. When the rotation speed of the rotation shaft 50 exceeds a predetermined value, the centrifugal force applied to the control pin 74a is greater than the pretension pressure of the valve plate 73a, and the control pin 74a moves toward the outside of the rotation shaft 50 to its actuation position against the pretension pressure of the valve plate 73a. At the actuation position of the control pin 74a, the control pin 74a lifts the valve plate 73a such that the valve plate 73a moves from its closed position to its open position, and the valve plate 73a leaves (or at least partially leaves) the oil drain hole 53a, thereby enabling a portion of the lubricating oil in the oil supply passage to be discharged to the outside of the rotary shaft 50 via the oil drain hole 53a and returned to the oil pool.

As will be appreciated by those skilled in the art, as the rotational speed of the rotating shaft 50 increases, the amount of oil entering the oil supply passage in the rotating shaft 50 also increases, and thus there is a risk of excessive oil supply. However, at the same time, the degree to which the control pin 74a protrudes out of the rotary shaft 50 increases, and the opening degree of the oil drain hole 53a increases accordingly, so that more lubricating oil in the oil supply passage can be discharged out of the rotary 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 be adapted to the rotation speed of the rotation shaft 50, prevent the oil circulation rate of the compressor from being excessively high, and realize balanced oil supply in the full rotation speed range. In addition, the control pin is independent of the control pin for controlling the opening and closing of the control valve, and the control pin can be manufactured and installed independently, so that the control pin is simple in structure, convenient to manufacture and install and easy to adjust and overhaul. In addition, the split design of pressure release hole and pinhole, pressure release hole and pinhole can process alone, and the design is nimble, simple process, low cost.

Preferably, a stop feature is provided at the pin bore 56a of the control pin 74a and/or the rotating shaft 50, such as a flange formed on the outer peripheral wall of the control pin 74a and a protrusion formed on the inner wall of the pin bore 56a that mates with the flange of the control pin 74a, thereby limiting the distance the control pin 74a protrudes out of the rotating shaft 50, avoiding the control pin 74a from disengaging from the rotating shaft 50 during extreme conditions.

Preferably, a main body portion 733a corresponding to the position of the oil drain hole 53a and a protrusion 734a extending outward from the main body portion 733a corresponding to the position of the pin hole 56a are formed at the movable end 732a of the valve plate 73a. The control pin 74a lifts the protruding portion 734a to separate the main body portion 733a from the oil drain hole 53a, thereby opening the oil drain hole 53a. The design makes the valve block of jacking up more easily of control pin to can keep more arrangement space for pressure release hole and pinhole as required, the shape and the size design of pressure release hole are more nimble.

Further, although the mounting holes 55 and the pin holes 56a are shown as being located at the upper and lower sides of the drain hole 53a, respectively, it will be understood by those skilled in the art that the mounting holes and the pin holes may be located at the left and right sides of the drain hole 53a, respectively, and even at one side of the drain hole 53a, as long as the mounting holes, the pin holes, and the drain hole 53a are arranged along the extending direction of the valve sheet. In this context, the extending direction of the valve sheet refers to the direction in which the valve sheet extends between its fixed end and movable end, and is not limited to the axial direction along the rotation axis shown in the embodiment of the present invention. But preferably the pin hole is further away from the fixed end of the valve plate than the drain hole 53a, so that the valve plate is more easily lifted up. In addition, the valve plate preferably extends in the axial direction of the rotary shaft, and the fixed end is located above the oil drain hole, and the pin hole is located below the oil drain hole, so that the lubricating oil is more easily discharged from the oil drain hole under the action of centrifugal force and the discharged lubricating oil is more easily returned to the oil sump.

Fig. 5 to 7 show a second embodiment according to the present invention. In the second embodiment according to the present invention, the overall construction and operation principle of the compressor are substantially the same as those of the first embodiment according to the present invention, and will not be described again. Unlike the first embodiment according to the present invention, the control pin in the oil supply control device according to the second embodiment of the present invention is not accommodated in a separate pin hole but is directly held in the drain hole.

Referring to fig. 5 and 6, the holding control device is provided in the mounting area S of the rotary shaft 50 as shown in detail C in fig. 5. The oil supply control device includes a drain hole 53b formed in the rotary shaft 50, a control valve 70b fixed to the rotary shaft 50, and a control pin 74b movably held on the rotary shaft 50. The oil drain hole 53b is configured to extend substantially in the radial direction of the rotary shaft 50 and to communicate the center passage 51 with the outer space of the rotary shaft 50. The rotary shaft 50 is also formed therein with a mounting hole 55 (blind hole) located above the drain hole 53b, wherein the mounting hole 55 is for fixing the control valve 70b, and the control pin 74b is directly accommodated in the drain hole 53b.

Referring to fig. 6, the control valve 70b is configured 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 sheet 73b and corresponds to the shape of the valve sheet 73b for protecting the valve sheet 73b. The valve plate 73b includes a fixed end 731b and a movable end 732b, and a through hole is formed at the fixed end 731b thereof. Accordingly, the valve cover 71b also includes a fixed end 711b, at which a through hole is formed at the fixed end 711b thereof. The fastener 72b is inserted into the mounting hole 55 of the rotation shaft 50 after passing through the through hole at the fixed end 711b of the valve cover 71b and the through hole at the fixed end 731b of the valve sheet 73b in order to detachably fasten one end of the control valve 70b to the rotation shaft 50. The valve plate 73b can cover the drain hole 53b at the movable end 732b thereof.

The control pin 74b is held in the drain hole 53b and is movable relative to the rotary shaft 50 in a substantially radial direction of the rotary shaft 50 by centrifugal force. In order to constitute a bypass passage for the lubricating oil flowing out from the center passage 51 to the outside of the rotary shaft 50, a channel exists between the control pin 74b and the wall of the drain hole 53b, that is, the channel may be formed on the wall of the drain hole (for example, the channel 534b shown in fig. 7 formed on the inner wall of the drain hole 53 b), may be formed on the outer peripheral wall of the control pin, or may be formed on both the wall of the drain hole and the outer peripheral wall of the control pin. Additionally or alternatively, a hollow duct (not shown in the drawing) may be formed in the control pin 74b to serve as a bypass passage for the lubricating oil, the inlet end of the hollow duct communicating with the center passage 51, the outlet end of the hollow duct preferably being provided at a position capable of communicating with the outside of the rotary shaft 50 but not in contact with the valve plate 73b, so as to avoid that the outlet end of the hollow duct is blocked by the valve plate 73b when the control pin 74b lifts the valve plate 73b, thereby affecting smooth discharge of the lubricating oil. For example, the hollow passage includes a lateral section and a longitudinal section connected to each other, the lateral section communicating with the center passage 51, and the longitudinal section communicating with the outside of the rotary shaft 50, an outlet of the longitudinal section (i.e., an outlet of the center passage) being formed on the outer peripheral wall of the control pin 74b at a position near the radially outer end thereof, whereby the lubricant in the center passage 51 is not affected by the valve plate 73b when discharged through the hollow passage.

Referring to fig. 7, the drain hole 53b includes a first diameter portion 531b and a second diameter portion arranged from the inside to the outside in the radial direction of the rotary 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. Thereby, when the control pin 531b is fitted into the drain hole 53b, the control pin 531b is accommodated in the second diameter portion, and the radially inner end portion of the control pin 531b abuts on the stepped portion formed between the first diameter portion 531b and the second diameter portion, thereby preventing the control pin 531b from coming off the rotation shaft 50 into the center passage 51.

The second diameter portion may be configured in a smooth straight bore form or may be configured in a stepped form as shown. As shown in fig. 7, the second diameter portion includes a first flow passage section 532b located radially inward and a second flow passage section 533b located radially outward, and the cross-sectional area of the first flow passage section 532b is smaller than that of the second flow passage section 533b, so that the oil discharge amount is increased stepwise, and the purpose of increasing the rotation speed and the oil discharge amount is achieved. For example, the cross section of the first flow section is circular, and the cross section of the second flow section is elliptical or oblong, wherein the minor axis length of the cross section of the second flow section is equal to the diameter of the cross section of the first flow section, such that the control pin is held and guided by the hole wall on both sides in the minor axis direction within the second flow section. For another example, the first and second flow segments may each be circular in cross-section, with a plurality of (e.g., three or four) ridges formed on the bore wall of the second flow segment and distributed along the circumference of the second flow segment for retaining and guiding the control pin within the second flow segment.

In the case where the second diameter portion is configured in a stepped form, the control pin 74b has a non-actuated position entirely within the rotary shaft 50, a first actuated position partially protruding outside the rotary shaft 50, and a second actuated position protruding more outside the rotary shaft 50 than the first actuated position. In the case where the rotation shaft 50 is stationary or rotates at a low speed, the control pin 74b is completely accommodated inside the drain hole 53b to be in its non-actuated position, and the valve plate 73b is in its closed position, the valve plate 73b applies a pretension to the drain hole 53b to close the drain hole 53b, and the control pin 74b and the valve plate 73b are not in contact or contact but the force between them is smaller than the pretension of the valve plate 73b even to be zero. As the rotational speed of the rotation shaft 50 increases, the centrifugal force to which the control pin 74b is subjected increases. When the rotational speed of the rotation shaft 50 exceeds a predetermined value, the centrifugal force applied to the control pin 74b is greater than the pretensioning pressure of the valve plate 73b, and the control pin 74b moves toward the outside of the rotation shaft 50 to its first actuation position against the pretensioning pressure of the valve plate 73b. At the first actuation position of the control pin 74b, the control pin 74b lifts the valve plate 73b to open the oil drain hole 53b, and at this time, the flow area of the lubricant discharged through the oil drain hole 53b is the flow area in the first flow passage 532b (for example, a flow area formed by a channel between the control pin 74b and the wall of the oil drain hole 53b and/or a hollow channel formed in the control pin 74 b). When the rotation speed of the rotation shaft 50 further increases, the control pin 74b further moves outward to its second actuation position, and the second flow path 533b is exposed, the flow area of the lubricant discharged through the oil drain hole 53b is the flow area in the second flow path 532 b. Since the cross-sectional area of the second flow-through section 533b is larger than the cross-sectional area of the first flow-through section 532b, the flow area in the second flow-through section 532b includes not only a flow area constituted by, for example, a channel existing between the control pin 74b and the wall of the oil drain hole 53b and/or a hollow channel formed in the control pin 74b, but also a flow area constituted by an increased gap between the control pin 74b and the inner wall of the oil drain hole 53b (the increased gap refers to, for example, a gap between the control pin and the wall of the oil drain hole in the major axis direction of the elliptical/oblong second flow-through section). Meanwhile, since the degree to which the control pin 74b protrudes out of the rotary shaft 50 increases, the degree to which the drain hole 53b is opened increases, and therefore, the control pin 74b can drain more lubrication oil in the oil supply passage out of the rotary shaft 50 in its second actuation position than in its first actuation position.

Therefore, the oil supply control device according to the present invention can be adapted to the rotation speed of the rotation shaft 50, prevent the oil circulation rate of the compressor from being excessively high, and realize balanced oil supply in the full rotation speed range. In addition, because the control pin is directly arranged in the pressure relief hole, the design of the pin hole is omitted, and the processing and the installation are simpler and more convenient.

The figures only show two exemplary embodiments under the concept of the invention. Those skilled in the art will appreciate that the 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 oil drain hole may be a single hole or more than one hole. For another example, the relief aperture may be configured in a variety of shapes as desired, such as a circular, oblong, rectangular, and other suitable shape in cross-section. Preferably, the oil drain holes configured as a plurality of holes are arranged along the extending direction of the valve plate and/or the long edges of the oil drain holes configured as oblong or rectangular shapes are arranged along the extending direction of the valve plate, so that as the degree to which the valve plate is lifted up by the control pin increases, the opening degree of the oil drain holes also gradually increases, thereby achieving the purpose that the larger the rotation speed of the rotating shaft is, the larger the oil drain amount of the oil drain holes is.

The rotary machine according to the preferred embodiment of the present invention has been described above in connection with the specific embodiments. It will be understood that the above description is by way of example only and not by way of limitation, and that various modifications and alterations will occur to those skilled in the art in light of the above description without departing from the scope of the invention. Such variations and modifications are intended to be included within the scope of the present invention.

Claims (14)

1. A rotary machine including a rotary shaft (50) in which an oil supply passage extending substantially in an axial direction of the rotary shaft is provided, the rotary machine further including an oil supply control device (70 a, 70 b) including:

oil drain holes (53 a, 53 b) that are formed in the rotary shaft and that communicate the oil supply passage with an outside of the rotary shaft; and

an oil drain valve (70 a, 70 b) including a valve plate (73 a, 73 b),

the oil supply control device is characterized by further comprising a control piece, wherein the control piece is movably kept on the rotating shaft, so that the movement of the control piece can cause the valve piece to move between an opening position for opening the oil drain hole and a closing position for closing the oil drain hole.

2. The rotary machine of claim 1, wherein the control member is a control pin (74 a, 74 b).

3. The rotary machine according to claim 2, wherein the control pin (74 b) is held in the oil drain hole (53 b), a channel (534 b) exists between the control pin and a wall of the oil drain hole and/or a hollow duct is formed in the control pin to constitute a bypass passage for outflow of lubricating oil from the oil supply passage to an outside of the rotary shaft.

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

5. The rotary machine according to claim 4, wherein the second diameter portion is configured in a stepped form including a first flow-through section (532 b) located radially inward and a second flow-through section (533 b) located radially outward, the cross-sectional area of the first flow-through section being smaller than the cross-sectional area of the second flow-through section.

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

7. The rotary machine according to claim 6, wherein the valve plate includes a main body portion (733 a) corresponding to a position of the oil drain hole and a protruding portion (734 a) extending outward from the main body portion corresponding to a position of the pin hole.

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

9. The rotary machine according to any one of claims 1 to 8, wherein the drain hole is configured as a single hole or a plurality of holes arranged along an extending direction of the valve sheet.

10. The rotary machine according to any one of claims 1 to 8, wherein the drain hole is configured to have a rectangular cross section, a circular cross section, or an oblong cross section, in which case the long edge of the drain hole is arranged along the extending direction of the valve sheet.

11. The rotary machine of any one of claims 1 to 8, wherein the control pin and/or the rotating shaft is provided with a stop feature to prevent the control pin from disengaging the rotating shaft.

12. The rotary machine according to any one of claims 1 to 8, wherein the control pin has a non-actuated position within the rotary shaft and an actuated position protruding outside the rotary shaft, with the control pin in the non-actuated position, the valve plate is in the closed position and the valve plate applies a pre-compression force to the drain hole, with the rotational speed of the rotary shaft exceeding a predetermined value, the control pin moves to the actuated position, and the control pin moves the valve plate to the open position against the pre-compression force.

13. The rotary machine according to claim 12, wherein as the rotation speed of the rotary shaft increases, the degree to which the control pin protrudes out of the rotary shaft increases, so that the degree of opening of the oil drain hole also increases.

14. The rotary machine of any one of claims 1 to 8, wherein the rotary machine is a variable frequency scroll compressor (100).