Patent Application
20190316587
Pursuant to 35 U.S.C. § 119(a), this application claims the benefit of earlier filing date and right of priority to Korean Application No. 10-2018-0043510, filed on Apr. 13, 2018, the contents of which are incorporated by reference herein in their entirety.
The present invention relates to a motor-operated compressor.
Among various compression methods, a scroll compression method suitable for high compression ratio operation is mainly applied to motor-operated compressors. In a scroll-type motor-operated compressor, a motor part having a rotary motor is installed inside a sealed casing, and a compression part composed of a stationary scroll and an orbiting scroll is installed on one side of the motor part. The motor part and the compression part are connected to each other by a rotary shaft to transfer the rotational force of the motor part to the compression part. The rotational force transferred to the compression part enables the orbiting scroll to orbit relative to the stationary scroll so that a pair of two compression chambers each composed of a suction chamber, an intermediate pressure chamber, and a discharge chamber are formed and also refrigerant is suctioned into both of the compression chambers and then compressed and discharged at the same time.
A scroll-type compression applied to an automobile air conditioning system (hereinafter abbreviated as a motor-operated compressor) is mainly installed in a horizontally long shape because of the structure of an automobile engine room. The motor part and the compression part are arranged in a horizontal direction and connected to the rotary shaft. Thus, a main frame and a subframe for supporting the rotary shaft are horizontally provided on both sides of the motor part, and a main bearing is provided on the main frame to support a central portion of the rotary shaft. A sub-bearing is provided in the subframe to support one end of the rotary shaft.
An example of conventional motor-operated compressors is disclosed in U.S. Patent Publication No. 2014/0134032A1 (May 15, 2014). In the motor-operated compressor, a back pressure space is formed between the main frame and the orbiting scroll to support the orbiting scroll toward the stationary scroll by the pressure in the back pressure space.
However, the conventional motor-operated compressor as described above has a problem in that the number of components is increased because a sealing member is provided to seal the back pressure space. Furthermore, the number of components may be further increased because a conventional sealing member should be fastened to the main frame.
Also, in the conventional motor-operated compressor, as the back pressure space is sealed such that the pressure in the back pressure space is stagnated, oil cannot be smoothly supplied to the back pressure space, resulting in oil shortage. Thus, there is a problem in that a frictional loss occurs in the sealing member or bearing located inside the back pressure space.
Therefore, an aspect of the detailed description is to provide a motor-operated compressor capable of suppressing an increase in manufacturing cost due to the use of a sealing member by allowing a back pressure space to be formed even after the sealing member is removed.
Also, the present invention provides a motor-operated compressor capable of forming a back pressure space in an open shape to eliminate the use of a sealing member.
Also, the present invention provides a motor-operated compressor capable of smoothly supplying oil to a bearing surface by enabling a back pressure space having a relatively high pressure to communicate with an inner space of a casing having a relatively low pressure to maintain the internal pressure in the back pressure space while preventing stagnation of the internal pressure.
To achieve these and other advantages and in accordance with the purpose of this specification, as embodied and broadly described herein, there is provided a motor-operated compressor in which a plurality of scrolls is provided inside a casing and supported by a frame, any one of the plurality of scrolls is fastened to the frame, and the frame and the stationary scroll fastened to the frame are axially spaced apart at a certain interval to radially support a rotary shaft for transferring a rotational force of a driving motor.
Here, a shaft hole through which the rotary shaft passes may be formed in the frame, a bearing for radially supporting the rotary shaft may be disposed in the shaft hole, and the back pressure space and the inner space of the casing may communicate through a gap between an inner peripheral surface of the bearing and an outer peripheral surface of the rotary shaft.
In order to achieve the objectives of the present invention, there is also provided a motor-operated compressor including a casing having an inner space composed of a suction space and a discharge space, a first scroll provided in the inner space of the casing, a second scroll configured to orbit in engagement with the first scroll to form a pair of two compression chambers between the first scroll and the second scroll, a rotary shaft coupled to the second scroll and configured to transfer a rotational force of a driving motor to the second scroll, and an intermediate pressure space formed on one side of the second scroll to communicate with the discharge space, configured to accommodate oil flowing in from the discharge space to form back pressure supporting the second scroll toward the first scroll, and opened toward the suction space so that a portion of the accommodated oil flows out into the suction space.
Here, a frame forming the intermediate pressure space along with the second scroll may be further provided on one surface of the second scroll, a shaft hole through which the rotary shaft passes may be formed in the frame, a first bearing for radially supporting a first bearing part of the rotary shaft may be provided inside the shaft hole, and a first radial bearing surface may be formed between an inner peripheral surface of the first bearing and an outer peripheral surface of the first bearing part, and both ends of the first radial bearing surface may communicate with the intermediate pressure space and the suction space, respectively.
Also, an oil flow path may be longitudinally formed in the rotary shaft, the oil flow path may have one end communicating with the discharge space, and at least one oil supply hole may be formed radially through the rotary shaft from the oil flow path to an outer peripheral surface of the rotary shaft. The at least one oil supply hole may be located at a position along an axial length of the rotary shaft that is outside an axial range of the first bearing part, wherein the axial range of the first bearing part refers to an axial distance from one axial end of the first bearing part to an opposite axial end of the first bearing part.
Also, the oil flow path may have another end placed outside the axial range of the first bearing.
Also, an oil flow path may be longitudinally formed in the rotary shaft, the oil flow path may have one end communicating with the discharge space, and a plurality of oil supply holes may be formed to pass from the oil flow path to an outer peripheral surface of the rotary shaft, and at least one of the plurality of oil supply holes may be positioned within an axial range of the first bearing part.
Also, the oil supply hole placed within the axial range of the first bearing part may have a smaller inner diameter than those of oil supply holes placed outside the axial range of the first bearing part.
Also, the oil supply hole placed within the axial range of the first bearing part may be eccentrically placed toward the discharge space with respect to an axial center of the first bearing part.
Here, at least one bearing surface may be formed on an outer peripheral surface of the rotary shaft, and an oil flow path and an oil supply hole for guiding the oil of the discharge space to the bearing surface may be formed in the rotary shaft, and the intermediate pressure space may communicate with the discharge space through the oil flow path and the oil supply hole.
Also, an intermediate pressure hole communicating between the intermediate pressure space and the compression chambers may be formed in the second scroll.
Here, a space part forming the intermediate pressure space may be formed in the frame, a shaft hole through which the rotary shaft is to pass may be formed at a center of the space part, and a bearing for radially supporting the rotary shaft may be provided in the shaft hole, and the intermediate pressure space may communicate with the suction space through a gap between an outer peripheral surface of the rotary shaft and an inner peripheral surface of the bearing provided in the shaft hole.
In order to achieve the objectives of the present invention, there is also provided a motor-operated compressor including a casing having an inner space composed of a suction space and a discharge space; a first scroll provided in the inner space of the casing; a second scroll configured to orbit in engagement with the first scroll to form a pair of two compression chambers between the first scroll and the second scroll; a frame placed opposite to the first scroll with the second scroll being interposed therebetween; and a rotary shaft having a first bearing part radially supported by the frame, a second bearing part radially supported by the first scroll, and an eccentric part placed between the first bearing part and the second bearing part and eccentrically coupled to the second scroll, wherein an oil flow path having one end communicating with the discharge space is formed in the rotary shaft, at least one oil supply hole for guiding oil of the discharge space to the first bearing part, the second bearing part, and the eccentric part is formed to pass from the oil flow path to an outer peripheral surface of the rotary shaft, and the at least one oil supply hole includes a first oil supply hole formed within an axial range of the second bearing part; and a second oil supply hole formed within an axial range of the eccentric part, with the at least one oil supply hole being formed outside an axial range of the first bearing part.
Here, the oil flow path may be formed from one end of the rotary shaft forming the second bearing part up to and including the range of the eccentric part.
Also, a shaft support part protruding opposite to the compression chamber may be formed on the first scroll, the second bearing part of the rotary shaft being rotatably inserted into the shaft support part, and a communication hole for communicating between the oil flow path and the discharge space may be formed on the shaft support part.
Also, the rotary shaft may be configured to form a first radial bearing surface together with the frame, configured to form a second radial bearing surface together with the first scroll or the casing that forms the discharge space together with the first scroll, and configured to form a third radial bearing surface together with the second scroll, and oil having passed through the second radial bearing surface or the third radial bearing surface may be guided to the first radial bearing surface.
Also, the first radial bearing surface may have one end communicating with an intermediate pressure space provided between the frame and the second scroll and another end communicating with the suction space.
With the motor-operated compressor according to the present invention, it is possible to suppress an increase in manufacturing cost due to the use of a sealing member by removing the sealing member from a frame forming an intermediate pressure space.
Also, with the motor-operated compressor according to the present invention, it is possible to facilitate manufacture of a rotary shaft by reducing the length of an oil flow path of the rotary shaft and also decreasing the number of oil supply holes because no separate oil supply hole is formed in a bearing part corresponding to a shaft hole of a frame.
Also, with the motor-operated compressor according to the present invention, an intermediate pressure space and a suction space may communicate through a radial bearing surface by removing a sealing member for separating the intermediate pressure space from the suction space. Thus, it is possible to smoothly supply oil to a bearing surface by maintaining internal pressure in the intermediate pressure space while preventing stagnation of the internal pressure in the intermediate pressure space.
Hereinafter, a motor-operated compressor according to the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings.
As shown in
The casing 101 is placed in a horizontal direction with respect to a ground surface, and the driving motor 103, and thus the compression part 105 are arranged in the horizontal direction. For convenience, in the following description, the right of
The casing includes a main housing 111 in which the frame 102, the driving motor 103, and compression part 105 are installed and a rear housing 112 coupled to an open rear end of the main housing 111 to cover the main housing 111. A suction port 101a is formed in the main housing 111, and an exhaust port 101b is formed in the rear housing 112. A suction space S1 is formed in the main housing 111, and a discharge space S2 is formed in the rear housing 112.
The frame 102 is coupled to a front open end of the main housing 111. A first scroll 150, which will be described below, is fastened to and supported by a rear surface of the frame 102. A second scroll 160, which will be described below, is movably supported on the rear surface of the frame 102 to orbit between the first scroll 150 and the frame 102.
The driving motor 103 includes a stator 131 fastened in the main housing 111, a rotor 132 placed inside the stator 131 and configured to rotate due to an interaction with the stator 131, and a rotary shaft 133 coupled to the rotor 132 and configured to transfer the rotational force of the driving motor 103 to the compression part 105 while rotating together with the rotor 132.
The compression part 105 includes a stationary scroll (hereinafter referred to as a first scroll) 150 supported by the frame 102 and an orbiting scroll (hereinafter referred to as a second scroll) 160 provided between the frame 102 and the first scroll 150 and configured to form a pair of two compression chambers V between the first scroll 150 and the second scroll 160 while orbiting relative to the first scroll 150. An oldham ring 170 is provided between the frame 102 and the second scroll 160 as an anti-rotation mechanism for preventing rotation of the second scroll 160 coupled to the rotary shaft 133 while allowing the second scroll 160 to orbit relative to the first scroll 150.
In the first scroll 150, a stationary scroll end plate (hereinafter referred to as a stationary end plate) 151 is formed in a substantially circular plate shape, and a stationary scroll side wall (hereinafter referred to as a scroll side wall) 152 to be coupled to a frame side wall 122 is formed at an edge of the stationary end plate 151. A stationary wrap 153 constituting the compression chamber V in engagement with an orbiting wrap 162, which will be described below, is formed on a front surface of the stationary end plate 151, and a shaft support part 151a for supporting a second bearing part 133d of the rotary shaft 133, which will be described below, is formed on a rear surface of the stationary end plate 151.
A suction flow path 154 is formed on one side of the scroll side wall 152 to enable the suction space S1 to communicate with a suction chamber (not shown), and a discharge port 155 for communicating with a discharge chamber and discharging compressed refrigerant into the discharge space S2 is formed at the center of the stationary end plate 151.
In the second scroll 160, an orbiting scroll end plate (hereinafter referred to as an orbiting end plate) 161 is formed in a substantially circular plate shape, and an orbiting wrap constituting the compression chamber in engagement with the stationary wrap 153 is formed on the rear surface of the orbiting end plate 161.
Also, an intermediate pressure hole 161a for enabling communication between an intermediate pressure space S3 and a compression chamber (an intermediate pressure chamber) V, which will be described below, is formed at the center of the orbiting end plate 161. Through the intermediate pressure hole 161a, oil moving into the intermediate pressure space S3 is supplied to the compression chamber V. The intermediate pressure hole 161a will be described below together with the oil supply passage.
The orbiting wrap 162 as well as the stationary wrap 153 may be formed in an involute shape, but may be formed in a non-involute shape.
When power is applied to the driving motor 103 of the scroll compressor, the rotary shaft 133 rotates along with the rotor 132 to transfer a rotational force to the second scroll 160, and the second scroll 160 is orbited by the oldham ring 170. Thus, the compression chamber V is continuously moved toward the center, thereby decreasing the volume of the compression chamber V.
Then, refrigerant flows into the suction space S1 through the suction port 101a. The refrigerant that has flowed into the suction space S1 is suctioned into the compression chamber V through the suction flow path 154 via a flow path formed on the outer peripheral surface of the stator 131 and the inner peripheral surface of the main housing 111 or via a gap between the stator 131 and the rotor 132.
Then, this refrigerant is compressed by the first scroll 150 and the second scroll 160 and discharged into the discharge space S2. In the discharge space S2, oil is separated from the refrigerant. The refrigerant is discharged in a refrigeration cycle through the exhaust port 101b while the oil is supplied to the compression chamber and bearing surfaces through an oil supply passage Fo, which will be described below. The series of processes are repeated.
Since the scroll compressor according to the present invention is installed in a horizontal direction, the rotary shaft may be stably supported when being supported at two or more points. To this end, the rotary shaft may be supported at both sides with respect to the driving motor or may be supported at one side with respect to the driving motor. In the former case, the length of the compressor is relatively long while in the latter case, the length of the compressor is shortened.
That is, in order to support both ends of the rotary shaft, one end of the rotary shaft passing through the second scroll may be inserted into and supported by the first scroll or may be inserted, through the first scroll, into and supported by the rear housing. Therefore, the former case will be described first in this embodiment, and the latter case will be described later in another embodiment.
Referring to
The rear housing 112 is coupled to the cylindrical part 111a of the main housing 111 to seal the inside of the casing 101. The discharge space S2 is formed in the rear housing 112, and the exhaust port 101b is formed at one side of the discharge space S2. An oil separator (not shown) for separating oil from discharged refrigerant is separately installed inside or around the exhaust port 101b. Alternatively, an oil separation part is formed without a separate oil separator.
Here, the discharge space S2 has an oil separation part S21, which separates oil from refrigerant discharged from the compression chamber, formed in an upper portion and an oil storage part S22, which stores the oil separated by the oil separation part S21, formed in a lower portion. The oil storage part S22 is in fluid communication with the compression part 105 through the oil supply passage FO, which will be described below, and the oil of the oil storage part S22 is supplied to the compression part 105 or the rotary shaft 133.
As shown in
The shaft part 133a is press-fitted and coupled to a rotor core of the rotor 132.
The first bearing part 133b is rotatably coupled through a frame shaft hole 125, which will be described below. A first bearing 181, which is a bush bearing to be described later, is inserted into and coupled to the inner peripheral surface of the frame shaft hole 125. The outer peripheral surface of the first bearing part 133b forms a first radial bearing surface B1 together with the inner peripheral surface of the first bearing 181.
The eccentric part 133c is eccentrically formed extending from the first bearing part 133b to one end (hereinafter referred to as a first end) of the rotary shaft 133 and coupled through a rotary shaft coupling part 163 of the second scroll 160. The rotary shaft coupling part 163 is formed to pass through the center of the orbiting end plate 161. A third bearing 183, which is a bush bearing, is inserted into and coupled to the inner peripheral surface of the rotary shaft coupling part 163. The inner peripheral surface of the third bearing 183 forms a third radial bearing surface B3 together with the outer peripheral surface of the eccentric part 133c.
The second bearing part 133d extends further toward the first end from the eccentric part 133c and is rotatably inserted into the shaft support part 151a of the first scroll 150. A second bearing 182, which is a bush bearing, is inserted into and coupled to the inner peripheral surface of the shaft support part 151a. The inner peripheral surface of the second bearing 182 forms a second radial bearing surface B2 together with the outer peripheral surface of the second bearing part 133d. However, the second bearing 182 is not limited to a bush bearing. That is, a needle bearing may be used as the second bearing 182. The needle bearing may be utilized as an axial bearing, and thus it is possible to restrain the rotary shaft 133 from being pushed toward the other end (hereinafter referred to as a second end) to some extent.
Meanwhile, the shaft support part 151a protrudes from the center of the stationary end plate 151 of the first scroll 150 rearward, that is, toward the rear housing 112. However, the shaft support part 151a may be formed so as not to protrude from the stationary end plate 151. However, in this case, the stationary end plate 151 may be formed to have a greater thickness by the thickness of the shaft support part 151a.
Also, a communication hole 151b for enabling the inner space of the shaft support part 151a to communicate with the oil storage part S22 may be formed in the shaft support part 151a, and an oil supply pipe 141 coupled to face the oil storage part S22 may be connected to the communication hole 151b. However, the present invention is not limited to an oil supply pipe, and an oil supply groove may be formed on the bottom surface of the first scroll 150 or in the rear housing 112 and then connected to the communication hole 151b
Meanwhile, an oil flow path 142 constituting a portion of the oil supply passage Fo is formed in the rotary shaft 133, and a plurality of oil supply holes 142a and 142b are formed in the middle of the oil flow path 142 at regular intervals in the lengthwise direction.
The oil flow path 142 may be formed up to an intermediate position of the rotary shaft 133. That is, since the oil flow path 142 should communicate with a first oil supply hole 142a and a second oil supply hole 142b to be described below, the length or depth of the oil flow path 142 may be greater than that of the second oil supply hole 142b, which is an oil supply hole at the eccentric part side relatively far from one end of the rotary shaft 133 at the compression part side.
For example, since the second oil supply hole 142b, which will be described below, is formed within the range of the eccentric part 133c, the oil flow path 142 may also be formed from the end of the rotary shaft 133 at the compression part side (or an end at the second bearing part side) up to the range of the eccentric part 133c. Reference to an oil supply hole being “within the range” or “within the axial range” of the eccentric part or bearing part, refers to the oil supply hole extending through the rotary shaft at an axial position along the length of the rotary shaft that falls within an axial distance from one axial end of the eccentric part or other bearing part to an opposite axial end of the respective part. The oil is discharged only through the first oil supply hole 142a and the second oil supply hole 142b even if the oil flow path 142 is further formed to a certain depth beyond the second oil supply hole 142b. Therefore, it is not necessary to form the oil flow path 142 deeply up to or beyond the eccentric part. However, when the oil flow path 142 is formed to be longer toward the first bearing part, it is possible to reduce the weight of the rotary shaft and increase the motor efficiency.
The plurality of oil supply holes 142a and 142b may penetrate radially toward the outer peripheral surfaces of the second bearing part 133d and the eccentric part 133c so that the oil moving through the oil flow path 142 is guided to each bearing surface. The plurality of oil supply holes 142a and 142b may be formed within the axial ranges of the second bearing part 133d and the eccentric part 133c corresponding to the oil supply holes 142a and 142b. The axial ranges of the respective bearing parts refers to axial distances extending from one axial end to an opposite axial end of each bearing part. Based on the order in which the oil moves, among the plurality of oil supply holes, an oil supply hole formed in the second bearing part 133d is classified as the first oil supply hole 142a, and an oil supply hole formed in the eccentric part 133c is classified as the second oil supply hole 142b.
Meanwhile, as described above, the frame 102 is located between the driving motor 103 and the compression part 105 and axially support the second scroll 160.
Also, a frame end plate 121 is formed in the frame 102 in a disc shape. A frame side wall 122 to which the side wall 152 of the first scroll 150 is to be coupled is formed at an edge of a rear surface of the frame end plate 121, and an intermediate pressure space S3, which will be described below, is formed at the center of the rear surface of the frame end plate 121.
Also, a frame thrust surface 123, on which the second scroll 160 is to be mounted and by which the second scroll 160 is to be axially supported, may be formed on an inner side of the frame side wall 122, and a sealing member 191 for sealing the intermediate pressure space S3 may be provided in the frame thrust surface 123. Since the sealing member 191 is provided on a thrust surface between the frame 102 and the second scroll 160, the sealing member 191 may be provided on the bottom surface of the second scroll 160.
Here, the intermediate pressure space S3 is a space formed between the rear surface of the frame 102 and the orbiting end plate 161 of the second scroll 160, which face each other. The intermediate pressure space is formed to always communicate with the intermediate pressure hole 161a of the second scroll 160.
Thus, the intermediate pressure space S3 is in fluid communication with the compression chamber (the intermediate pressure chamber) V through the intermediate pressure hole 161a such that refrigerant or oil moves between the intermediate pressure space S3 and the compression chamber V depending on a difference in pressure between the intermediate pressure space S3 and the compression chamber V. accordingly, the pressure in the intermediate pressure space S3 is equal to an intermediate pressure between the pressure in the suction space S1 and the final pressure (i.e., discharged pressure) in the compression chamber V, and the rear surface of the second scroll 160 is supported by the back pressure in the intermediate pressure space S3.
Also, the above-described frame shaft hole 125 is formed at the center of the frame 102 forming the intermediate pressure space S3. A first bearing 181, which forms a first radial bearing surface B1 along with the outer peripheral surface of the rotary shaft 133, i.e., specifically, the outer peripheral surface of the first bearing part 133b, may be inserted into and coupled to the inner peripheral surface of the frame shaft hole 125.
Also, a fine lubricating interval t1 is formed on the first radial bearing surface B1 placed between the outer peripheral surface of the first bearing part 133b and the inner peripheral surface of the first bearing 181. The intermediate pressure space S3 and the suction space S1 may communicate with each other through the lubricating interval t1.
As described above, when the first radial bearing surface B1 is sealed using a separate sealing member, the number of components is decreased due to the addition of the sealing member, and also new oil is prevented from flowing into the intermediate pressure space S3 because the pressure in the intermediate pressure space S3 is stagnated due to separation of the intermediate pressure space S3 from the suction space S1.
Thus, the oil can not be rapidly supplied to the compression chamber V communicating with the intermediate pressure space S3 such that the stationary wrap 153 and the orbiting wrap 162 may be worn or a frictional loss may occur. Furthermore, oil cannot be supplied even to the first radial bearing surface B1 communicating with the intermediate pressure space S3 such that friction losses may occur between the first bearing part 133b and the first bearing 181.
However, like this embodiment, when a gap between the first bearing part 133b and the first bearing 181 are opened without being sealed, the intermediate pressure space S3 communicates with the suction space S1 through the fine lubricating interval t1 formed on the first radial bearing surface B1, as shown in
Thus, the discharge space S2 communicates with the suction space S1 and the compression chamber V through the intermediate pressure hole 161a provided in the second scroll 160 and the radial bearing surfaces B2, B3, and B1 consisting of the oil supply passage.
Thus, the oil of the discharge space S2 moves to the intermediate pressure space S3 through the second and third bearing surfaces B2 and B3, and the oil having moved to the intermediate pressure space S3 forms a kind of back pressure in the intermediate pressure space S3 to support the second scroll 160 toward the first scroll 150.
In addition, a portion of the oil of the intermediate pressure space S3 is supplied to the compression chamber V through the intermediate pressure hole 161a to lubricate a gap between the stationary wrap 153 and the orbiting wrap 162 while another portion thereof flows out into the suction space S1 through the first radial bearing surface B1.
Thus, as the pressure in the intermediate pressure space S3 forms a flowing pressure, the oil of the discharge space S2 continuously moves to the intermediate pressure space S3. This oil may be circulated by moving to the compression chamber V and the suction space S1 through the intermediate pressure hole 161a and the first radial bearing surface B1, respectively.
In this case, an oil supply hole of the rotary shaft 133 is formed within the ranges of the eccentric part 133c and the second bearing part 133d forming the second radial bearing surface B2 and the third radial bearing surface B3, but is not formed within the range of the first bearing part 133b forming the first radial bearing surface B1.
When an oil supply hole is formed even within the range of the first bearing part 133b, the discharge space S2 directly communicates with the suction space S1 even though the pressure in the discharge space S2 is much higher than that in the suction space S1. Thus, the oil of the discharge space S2 quickly flows out into the suction space S1 such that the oil moves to the first and second oil supply holes 142a and 142b little or not at all. In this case, oil cannot be smoothly supplied to the second radial bearing surface B2 or the third radial bearing surface B3. This may cause friction losses in the second bearing 182 and the third bearing 183. In addition, the amount of oil flowing into the intermediate pressure space S3 becomes insufficient, so that oil supplied to the compression chamber V may become insufficient, or back pressure may not be secured, thereby causing axial leakage in the compression chamber V when the compressor is activated.
Therefore, as described above, in some embodiments, no oil supply hole may be formed within the range of the first bearing part 133b, and the oil supply holes 142a and 142b may be formed within the ranges of only the second bearing part 133d and the eccentric part 133c, respectively.
However, in alternative embodiments, an oil supply hole may be formed in the axial range of the first bearing part 133b in order for oil to be quickly supplied even to the first bearing part 133b.
As an example, as shown in
Accordingly, it is possible to reduce the pressure and amount of oil flowing to the first radial bearing surface B1 through the third oil supply hole 142c. In this case, it is possible to prevent more oil from moving to the third oil supply hole 142c than to the other oil supply holes 142a and 142b while quickly supplying oil to the first radial bearing surface B1, compared to the aforementioned embodiment. Thus, it is possible to uniformly supply oil to each of the bearing surfaces B1, B2, and B3 and also appropriately maintain the back pressure in the intermediate pressure space S3.
As another example, as shown in
Thus, a communication distance from the third oil supply hole 142c to the suction space S1 through the first radial bearing surface B1 increases. As a result, the same effect as in the previous embodiment can be expected.
Although not shown, the third oil supply hole 142c may be placed outside the range of the first bearing part 133b, that is, between the first bearing part 133b and the eccentric part 133c. In this case, the same effect as in the aforementioned embodiments can be expected.
Meanwhile, a pressure reducing part may be formed in the oil supply passage Fo.
For example, the oil supply passage Fo has an entrance communicating with the discharge space S2 (specifically, an oil storage), which is a high pressure part, and an exit communicating with the suction space S1, which is a low pressure part. Thus, when the pressure reducing part is not provided in the oil supply passage Fo, the oil of the discharge space S2 may excessively flow out into the suction space S1.
In view of this, a pressure reducing member 143 such as a pressure reducing bar is inserted into the oil flow path 142 constituting the oil supply passage Fo to narrow the inner diameter of the oil flow path 142, thereby lowering the pressure of oil passing through a pressure reducing section to an intermediate pressure. The pressure reducing member 143 may be placed not only inside the rotary shaft 133 but also anywhere in the upper stream with respect to the oil supply holes 142a and 142b.
However, as described above, the oil of the discharge space is depressurized while passing through the second radial bearing surface, the third radial bearing surface, and the first radial bearing surface, and thus a separate pressure reducing part may not be provided.
Meanwhile, another embodiment of the scroll compressor according to the present invention is as follows.
That is, according to the above-described embodiment, an intermediate pressure space is formed between a frame and a second scroll, and a balance weight 135 is provided outside the frame, i.e., outside the intermediate pressure space. However, according to this embodiment, a space part 124 forming the intermediate pressure space is recessed from the frame by a predetermined depth to form a back pressure space, and a balance weight 135 is accommodated in the back pressure space.
As shown, according to this embodiment, a space part 124 forming the intermediate pressure space S3 is formed at the center of the rear surface of the frame 102, as described above, and the frame shaft hole 125 may be formed to pass through the center of the space part 124.
The first bearing 181 is inserted into and fastened to the inner peripheral surface of the frame shaft hole 125. The first radial bearing surface B1 is formed between the inner peripheral surface of the first bearing 181 and the corresponding outer peripheral surface of the first bearing part 133b.
Here, since no sealing member is provided between the inner peripheral surface of the first bearing 181 and the corresponding outer peripheral surface of the first bearing part 133b, the first radial bearing surface B1 has one end communicating with the intermediate pressure space S3 and the other end communicating with the suction space S1, as in the above-described embodiment. Thus, the intermediate pressure space S3 communicates with the suction space S1 through the first radial bearing surface B1, and a portion of the oil flowing into the intermediate pressure space S3 flows out into the suction space S1. Thus, the internal pressure in the intermediate pressure space S3 forms a flowing pressure. Then, the oil of the discharge space S2 flows into the intermediate pressure space S3 through the oil flow path 142, the oil supply holes 142a and 142b, the second radial bearing surface B2, and the third radial bearing surface B3, and a portion of the oil moves to the compression chamber V through the intermediate pressure hole 161a, and a portion of other oil moves to the suction space S1 through the first radial bearing surface B1. The series of processes are repeated.
Even in such a case, the basic configuration and corresponding action effects are the same as those of the above-described embodiment, and thus a description thereof will be omitted.
Meanwhile, still another embodiment of the scroll compressor according to the present invention is as follows.
That is, in the aforementioned embodiments, the rotary shaft passes through the second scroll, which is an orbiting scroll, and is supported by the first scroll, which is a stationary scroll, or by the rear housing forming the casing. However, in the this embodiment, one end of the rotary shaft does not pass through the orbiting scroll and is coupled to a boss part provided on the bottom surface of the orbiting scroll.
In the scroll compressor according to this embodiment, as described above, the boss part is formed on the bottom surface of the second scroll, which is an orbiting scroll, and one end of the rotary shaft is eccentrically coupled to the boss part.
Also in this case, a back pressure space forming an intermediate pressure space may be formed between the second scroll and the frame, the frame shaft hole may be formed at the center of the back pressure space, and the first bearing may be inserted into and coupled to the inner peripheral surface of the frame shaft hole.
Also, since a sealing member is not provided between the inner peripheral surface of the frame shaft hole and the corresponding outer peripheral surface of the first bearing part, the back pressure space communicates with the suction space.
The basic configuration and corresponding action effects of the scroll compressor according to this embodiment are the same as those of the aforementioned embodiments, and a detailed description thereof will be omitted.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2018-0043510 | Apr 2018 | KR | national |
