CN217582496U - Rotary machine - Google Patents

Abstract

The utility model provides a rotary machine, this rotary machine include the rotation axis, are equipped with the oil supply passageway that roughly extends along the axial direction of rotation axis in the rotation axis, and rotary machine still includes fuel feeding control device, and fuel feeding control device includes: an oil drain hole formed in the rotary shaft and communicating the oil supply passage with an outside of the rotary shaft; and the oil drain valve comprises a valve plate, wherein the oil supply control device further comprises a control piece which is movably kept on the rotating shaft, so that the movement of the control piece can cause the valve plate to move between an opening position for opening the oil drain hole and a closing position for closing the oil drain hole. According to the utility model discloses a rotary machine can realize at balanced fuel feeding, stable performance reliable, the manufacturing and the maintenance of full rotational speed within range simple.

Description

Rotary machine

Technical Field

The utility model relates to an oil supply control device and rotating machinery who has this oil supply control device, more specifically relates to an oil supply control device and have oil supply control device's inverter compressor suitable for inverter compressor.

Background

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

In this context, rotary 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 rotary shaft for driving the compression mechanism. Generally, when a compressor is operated, a rotating shaft is rotated to drive a compression mechanism to compress a working fluid, while a lubricant is supplied to various moving parts (including a bearing, a bushing, a scroll, etc.) or a thrust surface of the compressor via an inner through hole of the rotating shaft. For example, it is necessary to supply lubricant (e.g., lubricating oil) between the orbiting and non-orbiting scroll members of the compression mechanism to improve friction between the orbiting and non-orbiting scroll members, thereby reducing wear and power consumption.

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

Although the oil circuit design can ensure oil supply under the condition of low speed of the compressor, 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 scroll compression cavity, the heat exchange efficiency of the compressor and a 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 cause a reduction in the oil sump liquid level within the compressor, affecting the reliability of the compressor.

Therefore, the utility model discloses it is expected to provide a satisfy the oil supply controlling means of the fuel feeding equilibrium of compressor in full rotational speed within range.

SUMMERY OF THE UTILITY MODEL

The general summary of the invention is provided in this section, not an exhaustive scope of the invention or a comprehensive disclosure of all of the features of the invention.

An object of the utility model is to provide a can balance the oil supply controlling means of the lubricating oil supply volume of compressor, especially avoid the too high oil supply controlling means of fuel feeding of compressor under the high rotational speed condition of compressor.

Another object of the utility model is to provide a rotating machinery, especially a frequency conversion compressor, this rotating machinery can realize the balanced fuel feeding at full rotational speed within range, avoids the too high efficiency that leads to of oil circulation rate to reduce or even trouble.

Another object of the present invention is to provide an oil supply control device and a rotary machine, which are easy to manufacture, replace, maintain and reduce costs.

The utility model provides a rotary machine, this rotary machine include the rotation axis, are equipped with the oil supply channel that roughly extends along the axial direction of rotation axis in the rotation axis, and rotary machine still includes fuel feeding control device, and fuel feeding control device includes: an oil drain hole formed in the rotary shaft and communicating the oil supply passage with an outside of the rotary shaft; and the oil drain valve comprises a valve plate, wherein the oil supply control device further comprises a control piece which is movably kept on the rotating shaft, so that the movement of the control piece can cause the valve plate to move between an opening position for opening the oil drain hole and a closing position for closing the oil drain hole.

Optionally, the control member is a control pin.

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

Alternatively, the oil release 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 the 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 on a radially inner side and a second flow-through section on a radially outer side, the first flow-through section having a cross-sectional area smaller than that of the second flow-through section.

Alternatively, a pin hole is additionally formed on the rotary shaft, the control pin is held in the pin hole, and the valve sheet 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 protrusion portion extending outward from the main body portion, the main body portion corresponds to a position of the oil drainage hole, and the protrusion portion corresponds to a position of the pin hole.

Optionally, the valve sheet includes a fixed end fixed to the rotation shaft and a movable end opposite to the fixed end, and the pin hole is farther from the fixed end than the oil drain hole.

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

Alternatively, the oil release hole is configured to have a rectangular cross section, a circular cross section, or an oblong cross section, and in the case of the rectangular cross section and the oblong cross section, the long side of the oil release hole is arranged along the extending direction of the valve sheet.

Optionally, the control pin and/or the rotation shaft is provided with a stop feature to avoid disengagement of the control pin from the rotation shaft.

Alternatively, the control pin has a non-actuated position inside the rotary shaft and an actuated position projecting outside the rotary shaft, and in the case where the control pin is in the non-actuated position, the valve sheet is in the closed position and the valve sheet applies a pretensioning pressure to the oil release hole, and in the case where the rotation speed of the rotary shaft exceeds a predetermined value, the control pin moves to the actuated position and moves the valve sheet to the open position against the pretensioning pressure.

Alternatively, 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 to which the oil release hole is opened also increases.

Optionally the rotary machine is a variable frequency scroll compressor.

Generally, according to the utility model discloses an oil supply control device and adopt this oil supply control device's rotating machinery bring following beneficial effect at least: 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 reliability of the rotary machine during low-speed running are maintained, and when the rotary machine runs at a high speed, the phenomenon that the oil supply is too high can be prevented, so that the energy efficiency and reliability of the rotary machine are prevented from being reduced; in addition, the oil supply amount can be adjusted in a self-adaptive manner according to different running rotating speeds of the rotary machine, so that balanced oil supply in the full rotating 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 with reference to the accompanying drawings, which are given by way of example only and which are not necessarily drawn to scale. The use of the same reference numbers in the figures indicates similar components, and wherein:

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 illustrates an exploded view of the oil supply control device and the rotating shaft according to the first embodiment of the present invention;

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

fig. 5 illustrates an exploded view of an oil supply control device and a rotating 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 is 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 designated by the same reference numerals throughout the several views. The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. In the drawings, the rotary machine is shown as a variable frequency scroll compressor, but it will be understood 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 rotary shaft, crankshaft or rotary shaft.

First, the general configuration 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, an inverter scroll compressor 100 (hereinafter sometimes referred to as a scroll compressor or compressor) generally includes a casing 10, a compression mechanism constituted by a fixed scroll part 20 and an orbiting scroll part 30, a main bearing housing 40, and a rotary shaft 50 and a motor 60 for driving the compression mechanism, and the like. The helical vanes of the orbiting scroll member 30 and the helical vanes of the non-orbiting scroll member 20 mesh with each other to form therebetween a series of compression chambers having a volume gradually decreasing from a radially outer side to a radially inner side. An end of the rotary shaft 50 adjacent to the orbiting scroll 30 is provided with an eccentric crank pin. An eccentric crank pin is inserted into the hub of orbiting scroll member 30. Driven by motor 60, rotating shaft 50 orbits orbiting scroll member 30 relative to non-orbiting scroll member 20 via an eccentric crank pin to effect compression of the working fluid.

Lubrication and cooling of the moving components of the scroll compressor 100, for example, lubrication and cooling of the spiral vanes of the orbiting scroll member 30 and the spiral vanes of the non-orbiting scroll member 20, are required. In the scroll compressor shown in fig. 1, the bottom of the casing 10 forms an oil sump for storing lubricating oil. Accordingly, the rotating 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 rotating 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 lubricating oil in the oil sump is supplied into the central passage 51 at the lower end of the rotary shaft 50, and the lubricating oil entering the central passage 51 is pumped or thrown into the eccentric passage 52 by centrifugal force during rotation of the rotary shaft 50 and flows upward along the eccentric passage 52 up to the end face of the eccentric crank pin. A portion of the lubricating oil discharged from the end face of the eccentric crank pin is used to lubricate components near the eccentric crank pin and the orbiting scroll hub and is then discharged out of main bearing housing 40 to return to the oil sump, and another portion is pushed to orbiting scroll oil passage 32 in the end plate of orbiting scroll component 30 that communicates with the compression chambers. Thus, the lubricating oil can enter the compression chamber from two ways: 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, oil droplets formed in the process of lubricating other components (e.g., the thrust surface of main bearing housing 40), and is thus sucked into the compression chamber along with the working fluid. These two approaches ensure that sufficient lubricating oil is supplied into the compression chamber, thereby ensuring sufficient lubrication between the movable scroll part 30 and the fixed scroll part 20, and particularly avoiding the problems of insufficient oil supply and failure proneness of the scroll compressor 100 in the case of low-speed operation.

However, when the scroll compressor 100 is operated at a high rotation speed, the amount of oil supplied to the oil supply passage in the rotating shaft 50 is rapidly increased, and the amount of oil entering the compression chambers through the orbiting scroll oil passage 32 is also rapidly increased, which may cause an excessive oil circulation rate of the compressor and affect the compressor and system energy efficiency. For this purpose, the rotating 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 mounting region S of the rotary shaft 50, as shown in detail B in fig. 3. In the installation region S, the outer surface of the rotary shaft 50 is formed as a slightly recessed plane with respect to the arc-shaped surface of the other region, thereby preventing the oil supply control means from excessively protruding from the outer surface of the rotary shaft 50 to affect other parts of the compressor and further facilitating the operation and installation of the control valve. The oil supply control device includes an oil release 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 implemented as the control pin 74a, but it will be understood by those skilled in the art that the control member may also be implemented in any other suitable form, such as a sphere. The oil release hole 53a communicates the central passage 51 with the outside space of the rotary shaft 50. Preferably, the oil release hole 53a is configured to extend substantially in the radial direction of the rotary shaft 50 so as to facilitate the discharge of the lubricating oil from the central passage 51 by the centrifugal force. In some other examples, the oil release hole may also be configured to communicate the eccentric passage 52 with the space outside the rotary shaft 50, and be provided on the opposite side of the central axis of the rotary shaft 50 with respect to the central axis of the eccentric passage 52, thereby facilitating discharge of a portion of the lubricating oil in the eccentric oil passage 52 to the outside of the rotary shaft under the action of centrifugal force. The rotary shaft 50 is also formed therein with a mounting hole 55 (blind hole) above the drain hole 53a, the mounting hole 55 being for fixing the control valve 70a, and a pin hole 56a (blind hole) below the drain hole 53a, the pin hole 56a being for receiving the control pin 74a. The pin hole 56a substantially conforms to the cross-sectional shape of the control pin 74a, and the cross-sectional dimension of the pin hole 56a is slightly larger than the cross-sectional dimension of the control pin 74a, so that the sliding movement of the control pin 74a can be guided by the hole wall of the pin hole 56a, thereby making the sliding movement of the control pin 74a smoother.

Referring to fig. 4, the control valve 70a is configured as a reed valve including a valve sheet 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. Valve sheet 73a includes a fixed end 731a and a movable end 732a, at fixed end 731a of which a through hole is formed. Accordingly, the valve cover 71a also includes a fixed end 711a at which a through hole is formed. The fastening member 72a is inserted into the mounting hole 55 of the rotating 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 rotating shaft 50. The valve sheet 73a can cover both the drain hole 53a and the pin hole 56a at its movable end 732 a.

The control pin 74a is held in the pin hole 56a and is movable relative to the rotary shaft 50 substantially in the radial direction of the rotary shaft 50 by the centrifugal force. The control pin 74a has a non-actuated position completely inside the rotating shaft 50 and an actuated position at least partially protruding outside the rotating shaft 50. When the rotating shaft 50 is at rest or rotates at a low speed, the control pin 74a is completely accommodated in the pin hole 56a and is in the non-actuated position, the valve plate 73a is in the closed position, the valve plate 73a applies a pre-tightening pressure to the oil release hole 53a and the pin hole 56a, so as to close the oil release hole 53a, and the control pin 74a and the valve plate 73a are not in contact or contact, but the acting force between the control pin 74a and the valve plate 73a is smaller than the pre-tightening pressure of the valve plate 73a, or even is zero. As the rotation speed of the rotating shaft 50 increases, the centrifugal force to which the control pin 74a is subjected increases. When the rotation speed of the rotating shaft 50 exceeds a predetermined value, the centrifugal force applied to the control pin 74a is greater than the preload pressure of the valve plate 73a, and the control pin 74a overcomes the preload pressure of the valve plate 73a and moves to the actuating position thereof toward the outer side of the rotating shaft 50. At the actuating position of the control pin 74a, the control pin 74a lifts up the valve sheet 73a so that the valve sheet 73a moves from its closed position to its open position, and the valve sheet 73a leaves (or at least partially leaves) the oil drain hole 53a, thereby enabling a part 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 to return to the oil pool.

It will be understood by those skilled in the art that as the rotational speed of the rotary shaft 50 increases, the amount of oil entering the oil supply passage in the rotary shaft 50 also increases, and thus there is a risk of an excessive supply of oil. At the same time, however, the degree of protrusion of the control pin 74a out of the rotary shaft 50 is also increased, and the opening degree of the oil release hole 53a is increased, so that more lubricant in the oil supply passage can be discharged out of the rotary shaft 50, thereby effectively preventing a large amount of lubricant from entering the compression chamber. Therefore, according to the utility model discloses an oil supply control device can be self-adaptive to the rotational speed of rotation axis 50, prevents that the oil circulation rate of compressor is too high, realizes the balanced fuel feeding in the full rotational speed scope. In addition, the opening and closing of the control valve are actuated by a control pin independent of the control valve, the control pin can be independently manufactured and installed, and the control valve is simple in structure, convenient to manufacture and install and easy to adjust and overhaul. In addition, the pressure relief holes and the pin holes are designed in a split mode, the pressure relief holes and the pin holes can be machined independently, and the pressure relief device is flexible in design, simple in process and low in cost.

Preferably, the control pin 74a and/or the pin hole 56a of the rotating shaft 50 are provided with stop features, such as a flange formed on the outer circumferential wall of the control pin 74a and a protrusion formed on the inner wall of the pin hole 56a to match the flange of the control pin 74a, so as to limit the distance that the control pin 74a protrudes out of the rotating shaft 50 and prevent the control pin 74a from being disengaged from the rotating shaft 50 in extreme operating conditions.

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

Further, although the mounting hole 55 and the pin hole 56a are shown in the drawings as being located on the upper and lower sides of the oil release hole 53a, respectively, it will be understood by those skilled in the art that the mounting hole and the pin hole may be located on the left and right sides of the oil release hole 53a, respectively, even on one side of the oil release hole 53a, as long as the mounting hole, the pin hole, and the oil release hole 53a are arranged along the extending direction of the valve sheet. Herein, the extending direction of the valve sheet refers to a direction in which the valve sheet extends between the fixed end and the movable end thereof, and is not limited to the axial direction along the rotation shaft shown in the embodiments of the present invention. But preferably, the pin hole is further away from the fixed end of the valve sheet than the oil release hole 53a, so that the valve sheet is more easily lifted. In addition, the valve sheet preferably extends along the axial direction of the rotation 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 likely to be discharged from the oil drain hole under the action of centrifugal force and the discharged lubricating oil is more likely to flow back to the oil sump.

Fig. 5 to 7 show a second embodiment according to the 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 the description thereof is omitted. Unlike the first embodiment according to the present invention, the control pin in the fuel supply control device according to the second embodiment of the present invention is not accommodated in a separate pin hole, but directly held in the drain hole.

Referring to fig. 5 and 6, the holding control means is provided in the mounting area S of the rotating shaft 50, as shown in detail C in fig. 5. The oil supply control device includes an oil release 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 release hole 53b is configured to extend substantially in the radial direction of the rotary shaft 50 and to communicate the central passage 51 with the outside space of the rotary shaft 50. The rotary shaft 50 is also formed therein with a mounting hole 55 (blind hole) above the 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 drain hole 53b.

Referring to fig. 6, the control valve 70b is configured as a reed valve including a valve sheet 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 sheet 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. The fastening member 72b is inserted into the mounting hole 55 of the rotating 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, thereby detachably fastening one end of the control valve 70b to the rotating shaft 50. The valve sheet 73b can cover the drain hole 53b at the movable end 732b thereof.

The control pin 74b is held in the oil release hole 53b and is movable relative to the rotary shaft 50 substantially in the radial direction of the rotary shaft 50 by the centrifugal force. In order to constitute a bypass passage for the outflow of the lubricating oil from the central passage 51 to the outside of the rotary shaft 50, a groove is present between the control pin 74b and the hole wall of the drain hole 53b, that is, the groove may be formed on the hole wall of the drain hole (for example, the groove 534b formed on the inner wall of the drain hole 53b shown in fig. 7), may be formed on the outer peripheral wall of the control pin, or may be formed on both the hole wall of the drain hole and the outer peripheral wall of the control pin. Additionally or alternatively, a hollow hole passage (not shown) may be formed in the control pin 74b to serve as a bypass passage for the lubricating oil, an inlet end of the hollow hole passage communicating with the central passage 51, and an outlet end of the hollow hole passage preferably being disposed at a position capable of communicating with the outside of the rotary shaft 50 but not contacting the valve sheet 73b, thereby preventing the outlet end of the hollow hole passage from being blocked by the valve sheet 73b when the control pin 74b pushes up the valve sheet 73b to affect smooth discharge of the lubricating oil. For example, the hollow hole includes a lateral section and a longitudinal section connected to each other, the lateral section communicating with the central passage 51, and the longitudinal section communicating with the outside of the rotary shaft 50, and an outlet of the longitudinal section (i.e., an outlet of the central hole) is formed on the outer peripheral wall of the control pin 74b at a position near the radially outer end thereof, whereby the lubricating oil in the central passage 51 is discharged through the hollow hole without being affected by the valve sheet 73b.

Referring to fig. 7, the oil release hole 53b includes a first diameter portion 531b and a second diameter portion arranged from inside to 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. Thus, when the control pin 531b is mounted into the oil release 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 step portion formed between the first diameter portion 531b and the second diameter portion, thereby avoiding the control pin 531b from coming off the rotary shaft 50 into the central passage 51.

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

In the case where the second diameter portion is configured in a stepped form, the control pin 74b has a non-actuated position located entirely inside the rotation shaft 50, a first actuated position projecting partially outside the rotation shaft 50, and a second actuated position projecting more outside the rotation shaft 50 than the first actuated position. In the case where the rotary shaft 50 is at rest or rotates at a low speed, the control pin 74b is completely accommodated inside the oil release hole 53b to be in its non-actuated position, and the valve plate 73b is in its closed position, and the valve plate 73b applies a biasing pressure to the oil release hole 53b to close the oil release hole 53b, and at this time, the control pin 74b and the valve plate 73b are not in contact or are in contact but the biasing pressure therebetween is smaller than that of the valve plate 73b or even zero. As the rotational speed of the rotary shaft 50 increases, the centrifugal force to which the control pin 74b is subjected increases. When the rotating speed of the rotating shaft 50 exceeds a predetermined value, the centrifugal force applied to the control pin 74b is greater than the pre-tightening pressure of the valve plate 73b, and the control pin 74b overcomes the pre-tightening pressure of the valve plate 73b and moves to the first actuating position of the rotating shaft 50 towards the outer side. At the first actuating position of the control pin 74b, the control pin 74b lifts up the valve sheet 73b to open the oil release hole 53b, and at this time, the flow area through which the lubricating oil is discharged via the oil release hole 53b is the flow area in the first flow path section 532b (for example, a flow area in which a groove is present between the control pin 74b and the hole wall of the oil release hole 53b and/or a hollow hole is formed in the control pin 74 b). When the rotational speed of the rotary shaft 50 further increases, the control pin 74b further moves outward to its second actuated position, and the second flow passage 533b is exposed, and at this time, the flow area through which the lubricating oil is discharged via the drain hole 53b is the flow area within the second flow passage 532 b. Since the cross-sectional area of the second flow-through section 533b is larger than that of the first flow-through section 532b, the flow-through area in the second flow-through section 532b includes not only a flow-through area constituted by, for example, a channel existing between the control pin 74b and the hole wall of the drain hole 53b and/or a hollow hole passage formed in the control pin 74b, but also a flow-through area constituted by an increased clearance between the control pin 74b and the inner wall of the drain hole 53b (the increased clearance refers to, for example, a clearance between the control pin and the hole wall of the drain hole in the major axis direction of the oval/oblong second flow-through section). Meanwhile, since the degree of protrusion of the control pin 74b out of the rotary shaft 50 increases, the degree of opening of the oil release hole 53b increases, and therefore, the control pin 74b can discharge more lubricant in the oil supply passage out of the rotary shaft 50 in its second actuated position than in its first actuated position.

Therefore, according to the utility model discloses an oil supply control device can be self-adaptive to the rotational speed of rotation axis 50, prevents that the oil circulation rate of compressor is too high, realizes the balanced fuel feeding in the full rotational speed scope. In addition, because the control pin is directly arranged in the pressure relief hole, the design of a pin hole is omitted, and the control pin is simple and convenient to machine and install.

The figures show only two exemplary embodiments under the inventive concept. It will be appreciated by persons skilled in the art that the present 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 drainage hole may be a single hole or more than one hole. As another example, the pressure relief vent may also be configured in a variety of shapes as desired, such as circular, oblong, rectangular, and other suitable shapes in cross-section. Preferably, the oil drainage hole that is constructed into a plurality of holes arranges along the extending direction of valve block and/or the long limit of the oil drainage hole that is constructed into obround or rectangle arranges along the extending direction of valve block for along with the valve block is increased by the degree of control pin jack-up, the degree of opening of oil drainage hole also crescent, thereby reach the purpose that the rotational speed of rotation axis is big more, the oil extraction volume of oil drainage hole is big more.

The rotary machine according to the preferred embodiment of the present invention has been described above with reference to the specific embodiments. It will be understood that the above description is intended to be illustrative and not restrictive, and that various changes and modifications may be suggested to one skilled in the art in view of the above description without departing from the scope of the invention. Such variations and modifications are also intended to be included within the scope of the present invention.

Claims (14)

1. A rotary machine comprising 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 comprising an oil supply control device comprising:

an oil drain hole formed in the rotary shaft and communicating the oil supply passage with an outside of the rotary shaft; and

the oil drain valve comprises a valve plate,

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

2. Rotating machine according to claim 1, wherein said control member is a control pin.

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

4. The rotary machine according to claim 3, wherein said oil drain hole includes a first diameter portion and a second diameter portion arranged from inside to outside in a radial direction of said rotary shaft, an inner diameter of said first diameter portion is smaller than an inner diameter of said second diameter portion, and an inner diameter of said first diameter portion is smaller than an outer diameter of said control pin.

5. The rotary machine of claim 4, wherein the second diameter portion is configured in a stepped manner including a first flow-through section on a radially inner side and a second flow-through section on a radially outer side, the first flow-through section having a smaller cross-sectional area than the second flow-through section.

6. The rotary machine of claim 2, wherein a pin hole is additionally formed on the rotary shaft, the control pin being retained in the pin hole, the valve plate covering both the oil drain hole and the pin hole in the closed position.

7. The rotary machine of claim 6, wherein the valve plate includes a main body corresponding to the position of the oil release hole and a protrusion extending outward from the main body corresponding to the position of the pin hole.

8. The rotary machine according to claim 6, wherein said valve plate includes a fixed end fixed to said rotary shaft and a movable end opposite to said fixed end, said pin hole being farther from said fixed end than said oil drain hole.

9. Rotating machine according to any of claims 1 to 8, characterized in that the oil drainage hole is configured as a single hole or a plurality of holes arranged along the extension of the valve plate.

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

11. Rotating machine according to any of claims 1 to 8, wherein the control pin and/or the rotating shaft are provided with a stop feature to avoid disengagement of the control pin from 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 inside the rotary shaft and an actuated position protruding outside the rotary shaft, and in the case where the control pin is in the non-actuated position, the valve sheet is in the closed position and the valve sheet applies a preload pressure to the oil drain hole, and in the case where the rotation speed of the rotary shaft exceeds a predetermined value, the control pin moves to the actuated position and the control pin moves the valve sheet to the open position against the preload pressure.

13. The rotary machine as claimed in claim 12, wherein as the rotation speed of said rotary shaft increases, the degree to which said control pin projects out of said rotary shaft increases, so that the degree to which said oil release hole is opened also increases.

14. The rotary machine of any one of claims 1 to 8, wherein the rotary machine is an inverter scroll compressor.

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