KR20230119433A - Compressor - Google Patents

Abstract

Compressor is started. The compressor is provided with a lead type discharge valve and a retainer for limiting the opening amount of the discharge valve, but the retainer fixing part constituting a part of the retainer is fixed outside the valve receiving groove provided in the fixed scroll or valve plate having the discharge port. It can be fastened to the back of. Through this, it is possible to reduce the discharge length of the discharge port to reduce the dead volume at the discharge port and at the same time secure the fastening depth to the retainer to suppress deformation of the fixed scroll.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor, and more particularly to a compressor having a reed type discharge valve.

The compressor forms a compression chamber to suck in refrigerant, compress the sucked refrigerant, and then discharge it. Accordingly, a suction port is provided on one side of the compression chamber, and a discharge port is provided on the other side.

Depending on the type of compressor, a suction valve may or may not be installed at the suction port. However, it is common that a discharge valve is installed at the discharge port.

As for the discharge valve, a plate valve (reed valve) or a piston valve (slip valve) is mainly applied depending on the type of compressor. The plate type valve has a simple structure and good valve response, while the piston valve can reduce the dead volume as the valve is inserted into the discharge port.

Patent Document 1 (Korean Patent Publication No. 10-2016-0034119) shows a reed valve applied to a compressor. The reed valve of Patent Document 1 is installed so that the discharge valve is detachable from the outer surface of the valve plate, and as the outer surface of the valve plate is formed flat, a dead volume is generated as much as the length of the discharge port.

In other words, in Patent Document 1, the high-pressure refrigerant remaining in the discharge port cannot escape into the discharge space during compression, and the high-pressure refrigerant flowing back to the compression chamber may decrease compression efficiency. Considering this, it is advantageous to minimize the volume of the discharge port by reducing the inner diameter of the discharge port or reducing the length of the discharge port. However, when the inner diameter of the discharge port is reduced, discharge resistance increases, and when the length of the discharge port is reduced, the thickness of the valve plate is reduced, and thus the fastening force for the discharge valve may be reduced.

Korean Patent Publication No. 10-2016-0034119 (published date: 2016.03.29.)

An object of the present invention is to provide a compressor capable of increasing compression efficiency by reducing dead volume when a reed type discharge valve is applied.

Furthermore, an object of the present invention is to provide a compressor capable of lowering the dead volume of the discharge port by reducing the discharge length of the discharge port.

Furthermore, an object of the present invention is to provide a compressor capable of securing fastening strength of the discharge valve while reducing the discharge length of the discharge port by reducing the thickness of the plate on which the discharge valve is mounted.

Furthermore, an object of the present invention is to provide a compressor capable of suppressing deformation due to the bolt fastening while fastening the discharge valve with bolts.

In order to achieve the object of the present invention, the compressor may include a casing, an orbiting scroll, a fixed scroll, a valve member and a retainer. The orbiting scroll is equipped with an orbiting wrap so that it can orbit in the casing. The fixed scroll may be provided with a fixed wrap engaged with the orbiting wrap to form a compression chamber, and may have a discharge port formed to discharge the refrigerant compressed in the compression chamber. One end of the valve member may be fixed to the fixed scroll, and the other end may open and close the discharge port. The retainer may be provided on a rear surface of the valve member and fixed to the fixed scroll. A valve receiving groove into which a part of the retainer is inserted together with the valve member may be formed on a rear surface of the fixed scroll facing the retainer. The retainer may include a retainer fixing part, a valve fixing part, and a valve support part. The retainer fixing part may be fastened to the fixed scroll. The valve fixing part may extend from the retainer fixing part and be inserted into the valve receiving groove to fix the valve member. The valve support portion may extend from the valve fixing portion and be inserted into the valve receiving groove to limit an opening amount of the valve member while being detachable from the valve member. The retainer fixing part may be fastened to the rear surface of the fixed scroll outside the valve receiving groove. Through this, it is possible to reduce the discharge length of the discharge port to reduce the dead volume at the discharge port and at the same time secure the fastening depth to the retainer to suppress deformation of the fixed scroll.

For example, the retainer fixing part may extend from both sides of the valve fixing part in a circumferential direction, and may be fastened to the rear surface of the fixed scroll at both sides of the valve receiving groove. Through this, since the retainer can be fastened outside the valve receiving groove, the discharge length of the discharge port can be reduced and the fastening strength of the retainer can be increased.

Specifically, a retainer fixing groove provided on both sides of the valve receiving groove in a circumferential direction may be formed on the rear surface of the fixed scroll and into which the retainer fixing part is inserted. A depth of the retainer fixing groove may be smaller than a depth of the valve receiving groove. Through this, it is possible to increase the fastening strength by securing the fastening depth to the retainer.

More specifically, a bolt fastening groove may be formed in the retainer fixing groove to fasten a fastening bolt penetrating the retainer. A plurality of bolt fastening grooves may be formed in each of the retainer fixing grooves. Through this, it is possible to suppress the deformation of the fixed scroll due to the bolt fastening by distributing the load generated during bolt fastening.

More specifically, the outer distance between the bolt fastening grooves on both sides located at the edge of the bolt fastening grooves may be formed equal to the inner distance between the two bolt fastening grooves located on the center side. Through this, it is possible to easily process the bolt fastening groove while securing fastening strength.

More specifically, the outer distance between the bolt fastening grooves on both sides located at the edge of the bolt fastening grooves may be larger than the inner distance between the bolt fastening grooves on both sides located at the center. Through this, it is possible to use relatively small bolts by increasing the overall fastening strength, which not only facilitates assembly but also suppresses deformation due to fastening of the bolts.

As another example, at least one bolt fastening groove for fastening the retainer may be formed on the rear surface of the fixed scroll. At least one of the bolt fastening grooves may overlap the fixing wrap in an axial direction. Through this, not only can the fastening depth be secured, but also the fastening strength can be further increased by distributing the load during fastening.

As another example, the outlet may be provided at one end of the valve receiving groove. A fixing pin may be provided at the other end of the valve receiving groove to be coupled to the valve member. Through this, it is possible to improve the compression efficiency by increasing the assemblability to the valve member and at the same time by increasing the bonding force to the valve member.

Specifically, a valve fixing hole through which the fixing pin passes may be formed in the valve member. A pin fixing groove may be formed in the retainer to insert the fixing pin penetrating the valve member. Through this, as both ends of the fixing pin are fixed, the supporting force of the fixing pin is improved, so that the discharge valve can be fixed more stably.

Specifically, a plurality of fixing pins may be provided at predetermined intervals in the radial direction. Through this, not only the supporting force for the discharge valve is improved by increasing the number of fixing pins, but also the valve fixing holes to which the fixing pins are coupled are arranged in the radial direction, so that damage to the valve due to the valve fixing holes can be suppressed.

As another example, the retainer fixing part may be formed thinner than the valve fixing part and the valve support part. Through this, it is possible to increase the fastening strength by securing the fastening depth of the fastening bolt for fixing the retainer.

As another example, the retainer fixing part and the valve fixing part may be integrally formed. Through this, not only can the retainer be easily manufactured, but also assemblyability can be improved.

As another example, the retainer fixing part may be assembled and coupled to the valve fixing part. Through this, not only can the shape of the retainer be modified in various ways, but also the degree of freedom in material selection can be increased.

Specifically, a coupling part may be formed between the retainer fixing part and the valve fixing part so that the retainer fixing part is fixed to the valve fixing part. Through this, it is possible to increase assembly reliability of the retainer while manufacturing the retainer as a separate type.

Specifically, the retainer fixing part may be formed of a different material from the valve fixing part. This reduces the weight of the retainer and at the same time reduces material costs.

As another example, the discharge port may include a first discharge port and a plurality of second discharge ports. The first discharge port may communicate with the discharge pressure chamber of the compression chamber. The plurality of second discharge ports communicate with the intermediate pressure chamber of the compression chamber and may be formed on both sides of the first discharge port, respectively. The retainer may be fixed to the fixed scroll at both sides of an imaginary line passing through the center of the first discharge port in a radial direction. The valve member may include a fixed end and an opening/closing end. The fixed end may be fixed to the fixed scroll. The opening/closing end may include an opening/closing end extending from the fixed end and having a first opening/closing part opening/closing the first outlet and a second opening/closing portion opening/closing the second outlet. The fixed end may be fixed between the fixed scroll and the retainer on an imaginary line passing through the center of the first discharge port in a radial direction. Through this, operation reliability of the valve member can be improved as the valve member has a plurality of opening/closing parts and is fixed on the center line of the valve member.

As another example, the valve member may include a fixed end and an opening/closing end. The fixed end may be fixed to the fixed scroll. The opening/closing end may extend from the fixed end and open/close the discharge port. The fixed end may be fixed between the fixed scroll and the retainer on an imaginary line passing through the center of the discharge port in a radial direction. Through this, operation reliability of the valve member can be improved as the valve member is fixed on the center line of the valve member.

In order to achieve the object of the present invention, a valve plate, a valve member and a retainer may be included. The valve plate may have at least one discharge port. One end of the valve member may have a fixed end fixed to the valve plate, and the other end may form an opening/closing end for opening/closing the discharge port while being detachable from the valve plate. The retainer is provided on the rear surface of the valve member, one end fixes the fixed end of the valve member to the valve plate, and the other end is spaced apart from the valve plate with the valve member interposed therebetween to control the opening amount of the valve member. can be limited A valve receiving groove may be formed in the valve plate to insert the valve member and a part of the retainer. The retainer may include a retainer fixing part, a valve fixing part, and a valve support part. The retainer fixing part may be fastened to the valve plate. The valve fixing part may extend from the retainer fixing part and be inserted into the valve receiving groove to fix the valve member. The valve support portion may extend from the valve fixing portion and be inserted into the valve receiving groove to limit an opening amount of the valve member while being detachable from the valve member. The retainer fixing part may be fastened to the rear surface of the valve plate outside the valve receiving groove. Through this, it is possible to reduce the discharge length of the discharge port to reduce the dead volume at the discharge port and at the same time secure the fastening depth to the retainer to suppress deformation of the valve plate.

For example, retainer fixing grooves provided on both sides of the valve receiving groove in a circumferential direction may be formed on the rear surface of the valve plate and into which another part of the retainer is inserted. A depth of the retainer fixing groove may be smaller than a depth of the valve receiving groove. Through this, since the retainer can be fastened outside the valve receiving groove, the discharge length of the discharge port can be reduced and the fastening strength of the retainer can be increased.

In the compressor according to the present invention, the retainer fixing part constituting a part of the retainer may be fastened to the rear surface of the fixed scroll outside the valve receiving groove provided in the fixed scroll having a discharge port. Through this, it is possible to reduce the discharge length of the discharge port to reduce the dead volume at the discharge port and at the same time secure the fastening depth to the retainer to suppress deformation of the fixed scroll.

In the compressor according to the present invention, the retainer fixing part extends from both sides of the valve fixing part in the circumferential direction, and can be fastened to the rear surface of the fixed scroll at both sides of the valve receiving groove. Through this, since the retainer can be fastened outside the valve receiving groove, the discharge length of the discharge port can be reduced and the fastening strength of the retainer can be increased.

In the compressor according to the present invention, at least one of the bolt fastening grooves provided on the rear surface of the fixed scroll may overlap with the fixed wrap in the axial direction. Through this, not only can the fastening depth be secured, but also the fastening strength can be further increased by distributing the load during fastening.

In the compressor according to the present invention, the valve receiving groove may be provided with a fixing pin so as to be coupled to the valve member. Through this, it is possible to improve the compression efficiency by increasing the assemblability to the valve member and at the same time by increasing the bonding force to the valve member.

In the compressor according to the present invention, the retainer fixing portion may be formed thinner than the valve fixing portion and the valve support portion. Through this, it is possible to increase the fastening strength by securing the fastening depth of the fastening bolt for fixing the retainer.

In the compressor according to the present invention, the retainer fixing portion and the valve fixing portion may be integrally formed. Through this, not only can the retainer be easily manufactured, but also assemblyability can be improved.

In the compressor according to the present invention, the retainer fixing part may be assembled and coupled to the valve fixing part. Through this, not only can the shape of the retainer be modified in various ways, but also the degree of freedom in material selection can be increased.

In the compressor according to the present invention, the fixed end of the valve member may be fixed between the fixed scroll and the retainer on an imaginary line passing through the center of the first discharge port in a radial direction. Through this, operation reliability of the valve member can be improved as the valve member has a plurality of opening/closing parts and is fixed on the center line of the valve member.

In the compressor according to the present invention, the fixed end of the valve member may be fixed between the fixed scroll and the retainer on an imaginary line passing through the center of the discharge port in a radial direction. Through this, operation reliability of the valve member can be improved as the valve member is fixed on the center line of the valve member.

1 is a cross-sectional view showing a scroll compressor according to an embodiment.
Figure 2 is an exploded perspective view of the scroll compressor according to Figure 1;
3 is an exploded perspective view of the discharge valve assembly according to the present embodiment;
Figure 4 is a perspective view showing a state in which the discharge valve member is assembled in Figure 3;
Figures 5a and 5b are schematic views showing embodiments of the valve mounting portion in Figure 4;
6 is a plan view of the fixed scroll shown in FIG. 3 from above;
Fig. 7 is a sectional view "IX-IX" of Fig. 6;
FIG. 8 is a sectional view "X-X" of FIG. 6;
Fig. 9 is a sectional view "XI-XI" of Fig. 6;
10 is an exploded perspective view of another embodiment of a discharge valve assembly;
Fig. 11 is an assembled plan view of Fig. 10;
Fig. 12 is a sectional view "XII-XII" of Fig. 11;

Hereinafter, a compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. The compressor according to the present invention will be described focusing on a lead type discharge valve applied to a horizontal scroll compressor constituting a typical air conditioning refrigeration cycle together with a condenser, an expander and an evaporator in a gas engine heat pump. However, the compressor according to the present invention is not necessarily applied only to horizontal scroll compressors, but may equally be applied to other types of compressors such as rotary compressors as well as vertical scroll compressors.

However, in the compressor according to the present invention, when a bypass hole (hereinafter referred to as a first bypass hole) for preventing overpressure is further formed around the discharge port, the discharge valve for opening and closing the discharge port and the first bypass for opening and closing the first bypass hole Although an example in which the pass valve is formed as a single body is mainly described, the discharge valve and the first bypass valve are not necessarily formed as a single body. For example, the same can be applied even when the discharge valve and the first bypass valve are provided separately. This can be equally applied even when the first bypass hole and the first bypass valve are excluded and only the discharge port and the discharge valve are provided.

In addition, the compressor according to the present invention will be described as an example of a scroll compressor having a capacity variable bypass hole (hereinafter referred to as a second bypass hole) and a bypass valve (hereinafter referred to as a second bypass valve) for opening and closing the bypass hole. It is not limited to a scroll compressor provided with two bypass holes and a second bypass valve. In other words, the same can be applied even when the second bypass hole and the second bypass valve are excluded.

1 is a cross-sectional view showing a scroll compressor according to the present embodiment, and FIG. 2 is an exploded perspective view of the scroll compressor according to FIG. 1 .

1 and 2, the scroll compressor according to this embodiment includes a casing 110, a driving shaft 120, an orbiting scroll 130 and a fixed scroll 140 constituting a compression unit.

The casing 110 includes a main housing 111 , a front housing 112 and a rear housing 113 . The casing 110 constitutes the external appearance of the compressor, and is disposed on one side of the clutch assembly 2 and is coupled to the clutch assembly 2 by a drive shaft 120 . Hereinafter, the side facing the clutch assembly 2 is defined as the front side, and the opposite side is defined as the rear side. Accordingly, the front housing 112 refers to a housing disposed on the side facing the clutch assembly 2, and the rear housing 113 refers to a housing disposed on the opposite side, respectively.

The main housing 111 is formed in a cylindrical shape with both ends open, and a compression unit is accommodated therein. In other words, the inner space of the main housing 111 forms a suction space 110a into which the refrigerant passing through the evaporator 40 is sucked. However, the intake space of the main housing 111 also forms an oil sump in which not only the refrigerant but also the oil lubricating the sliding part including the compression part is stored.

One end (front end) of the main housing 111 is covered with the front housing 112 coupled thereto, and the other end (rear end) of the main housing 111 is covered with the rear housing 113 coupled thereto. Accordingly, the inner space of the main housing 111 is sealed by the front housing 112 and the rear housing 113 . However, as the driving shaft 120 passes through and is coupled to the front housing 112, a shaft sealing member 184 to be described later is provided between the front housing 112 and the driving shaft 120. Accordingly, the front end of the main housing 111 is sealed by the front housing 112 and the shaft sealing member 184, but hereinafter, for convenience, one end of the main housing 111 is sealed by the front housing 112. do.

The front housing 112 and the rear housing 113 may be welded to the main housing 111 or may be bolted together. In this embodiment, an example in which the front housing 112 and the rear housing 113 are bolted to the main housing 111 will be mainly described.

A first connecting protrusion (not marked) is formed on the outer circumferential surface of the main housing 111, that is, on the outer circumferential surface between the first housing protrusion 111a and the second housing protrusion 111b. A refrigerant intake port 1111 penetrating between an outer surface and an inner surface of the main housing 111 is formed in the first connection protrusion (not marked). The outer end of the refrigerant suction port 1111 is connected to the refrigerant suction pipe 115, and the inner end of the refrigerant suction port 1111 is opened to the inner circumferential surface of the main housing 111. Accordingly, the refrigerant suction pipe 115 communicates with the inner space of the casing 110 through the refrigerant suction port 1111, that is, the suction space 110a.

The refrigerant suction port 1111 may be formed at an intermediate position of the main housing 111, but may be formed as close as possible to the first suction end 132a, which will be described later. For example, the refrigerant suction port 1111 may be formed to be closer to the second housing protrusion 111b than the first housing protrusion 111a. Accordingly, the refrigerant suction port 1111 is brought closer to the first suction end 132a to be described later, so that the suction resistance of the refrigerant sucked into the compression chamber V through the refrigerant suction port 1111 can be reduced.

A second connection protrusion (not marked) is formed between the outer circumferential surface of the main housing 111, that is, between the first housing protrusion 111a and the second housing protrusion 111b. A return port 1112 penetrating between the outer and inner surfaces of the main housing 111 is formed in the second connection protrusion. The outer end of the return port 1112 is connected to the refrigerant recovery pipe (or oil return pipe) 151, and the inner end of the return port 1112 is opened to the inner circumferential surface of the main housing 111. Accordingly, the refrigerant recovery pipe (or oil return pipe) 151 communicates with the inner space of the casing 110, that is, the suction space 110a, through the return port 1112.

The front housing 112 is coupled to the front end of the main housing 111 to seal the inner space of the main housing 111, that is, the suction space 110a, and at the same time supports the orbiting scroll 130 in the axial direction. Accordingly, the front housing 112 may be understood as a part of the casing 110 or may be understood as a frame forming a part of the compression unit.

The front housing 112 may be made of aluminum to reduce the weight of the compressor when applied to a vehicle. However, since the compressor used for building air conditioning is fixedly installed in an outdoor unit, the front housing 112 may be made of cast iron instead of aluminum. Accordingly, the reliability of the compressor for building air conditioning, which has a higher load than that for vehicles, can be improved.

Specifically, the front housing 112 according to the present embodiment includes a cover part 1121 and a frame part 1122. The cover part 1121 is a part of the casing 110, and the frame part 1122 is a part of the compression part.

The cover part 1121 and the frame part 1122 may be integrally formed or may be assembled separately. Although the present embodiment shows an example in which the cover part 1121 and the frame part 1122 are integrally formed, the same can be applied even when the cover part 1121 and the frame part 1122 are separately assembled.

A bearing portion 1121b is formed through the cover portion 1121. The shaft accommodating portion 1121b is formed on the same axis as the turning space portion 1122a of the frame portion 1122 to be described later. Accordingly, the drive shaft 120 passes through the shaft accommodating portion 1121b of the cover portion 1121 and the turning space portion 1122a of the frame portion 1122, the front end of the clutch assembly 2, and the rear end of the turning scroll. (130), respectively.

The shaft accommodating portion 1121b may be formed in multiple stages. For example, the front side of the shaft accommodating portion 1121b may have a small inner diameter and the rear side may have a large inner diameter. A first support bearing 185 supporting the front side of the driving shaft 120 is provided in the front shaft receiving portion 1121b1, and a second support bearing 185 supporting the rear side of the driving shaft 120 is located in the rear shaft receiving portion 1121b2. Bearings 186 may be provided respectively.

In addition, a lubrication space 1121c may be formed on one side of the shaft accommodating portion 1121b, that is, between the front shaft accommodating portion 1121b1 and the rear shaft accommodating portion 1121b2. The inner diameter of the lubrication space portion 1121c may be larger than the inner diameter of the front shaft accommodating portion 1121b1 and smaller than the inner diameter of the rear shaft accommodating portion 1121b2. Accordingly, the inner diameter may be formed to gradually increase from the front shaft accommodating portion 1121b1 to the rear shaft accommodating portion 1121b2 via the lubrication space portion 1121c.

A shaft sealing member 184 is provided in the lubrication space 1121c. Specifically, the shaft sealing member 184 may be located between the first support bearing 185 and the second support bearing 186, that is, between the lubrication space portion 1121c and the front shaft receiving portion 1121b1. there is. Accordingly, a portion of the shaft sealing member 184 is positioned in the front side shaft accommodating portion 1121b1, and the other portion is positioned in the lubrication space portion 1121c.

The frame portion 1122 is formed in an annular shape, and a turning space portion 1122a is formed in the central portion. The orbiting space portion 1122a is a space in which the drive shaft coupling portion 133 of the orbiting scroll 130, which will be described later, performs a pivoting motion, and is penetrated so as to communicate with the shaft accommodating portion 1121b and the lubrication space portion 1121c on the same axis. .

The rear surface of the frame portion 1122 forms a scroll support surface 1122b. In other words, the rear surface of the frame portion 1122 facing the orbiting scroll 130 forms a scroll support surface 1122b on which the orbiting mirror plate portion 131 to be described later is axially supported. Accordingly, the scroll support surface 1122b forms the aforementioned axial bearing surface together with the front surface of the turning mirror plate portion 131 facing it.

The entire scroll support surface 1122b may be formed flat to be flat, or at least one oil supply groove 1122c may be formed such that the scroll support surface 1122b is uneven. The oil supply groove may be formed on the front surface of the turning mirror plate part 131 facing the scroll support surface 1122b. In this embodiment, an example in which the oil supply groove 1122c is formed on the scroll support surface 1122b is shown.

Meanwhile, an anti-rotation pin 171 constituting the anti-rotation mechanism 170 is provided on the scroll support surface 1122b together with a ring insertion groove (or an anti-rotation ring) to be described later. The anti-rotation pins 171 are provided in plurality and are provided at predetermined intervals along the circumferential direction, for example, between oil supply grooves 1122c to be described later. Accordingly, the anti-rotation pin 171 together with the ring insertion groove (or anti-rotation ring) 1311 to be described later suppresses the rotation of the orbiting scroll 130.

At the same time, the oil stored in the suction space 110a of the casing 110, that is, the storage space constituting the lower half of the suction space 110a, passes through the oil supply groove 1122c to the front housing 112 and the orbiting scroll 130. (Between the thrust plate 135 and the front housing 112 to be precise, and between the thrust plate 135 and the orbiting scroll 130, which will be described later).

The anti-rotation pin 171 may extend as a single unit from the rear surface of the frame unit 1122 toward the orbiting scroll 130, or may be manufactured separately and then assembled. In this embodiment, an example in which the anti-rotation pin is press-fitted into the frame portion 1122 is shown.

The rear housing 113 according to this embodiment is formed in a substantially cylindrical shape with one end (front end) open and the other end (rear end) closed. In other words, the front end facing the fixed scroll 140 to be described later is open, while the rear end facing the fixed scroll 140 is closed. Accordingly, the inner space of the rear housing 113 forms a discharge space 110b together with the rear surface of the fixed end plate 141 to be described later, so that the refrigerant discharged from the compression chamber V is accommodated.

At the front end of the rear housing 113, a third housing protrusion 113a, which is bolted to the aforementioned second housing protrusion 111b, extends in a flange shape. The second sealing member 182 described above is inserted between the third housing protrusion 113a and the second housing protrusion 111b and fastened with bolts along the circumferential direction.

Although not shown in the drawings, a spacer (not shown) may be provided between the second housing protrusion 111b and the rear housing 113 to be fastened with bolts. In this case, a sealing protrusion (not shown) extends toward the main housing 111 at the front end of the rear housing 113, and a second sealing member (not shown) is formed between the outer circumferential surface of the sealing protrusion and the inner circumferential surface of the main housing 111 facing it. not shown) may be provided.

A third connection protrusion (unsigned) and a fourth connection protrusion (unsigned) are formed at the closed rear end of the rear housing 113. The third connection protrusion is formed at the center of the rear end of the rear housing 113, and the fourth connection protrusion is formed around the third connection protrusion. A refrigerant discharge port 1131 is formed in the third connection protrusion, and a bypass port 1132 is formed in the fourth connection protrusion. The refrigerant discharge port 1131 and the bypass port 1132 penetrate between the inner and outer surfaces of the rear housing 113, respectively.

The inner end of the refrigerant discharge port 1131 is opened to the inner circumferential surface of the rear housing 113 to communicate with a discharge port 1411 to be described later, and the outer end of the refrigerant discharge port 1131 is connected to the refrigerant discharge pipe 116. Accordingly, the refrigerant discharge pipe 116 communicates with the inner space of the rear housing 113, that is, the discharge space 110b through the refrigerant discharge port 1131. The refrigerant discharge pipe 116 is connected to the inlet of the previously described oil separator (not shown).

The inner end of the bypass port 1132 is opened to the inner circumferential surface of the rear housing 113 to communicate with the bypass guide groove 1411c to be described later, and the outer end of the bypass port 1132 is connected to the refrigerant recovery pipe 151. . Accordingly, the inner space of the rear housing 113, that is, the bypass guide groove 1411c communicates with the refrigerant recovery pipe 151 through the bypass port 1132. The refrigerant recovery pipe 151 may be directly connected to the return port 1112 of the main housing 111 described above or connected through an oil return pipe (not shown).

The drive shaft 120 according to this embodiment transmits the driving force transmitted through the clutch assembly 2 to the compression unit, that is, to the orbiting scroll 130, and a part of the drive shaft 120 is outside the casing 110. , Other parts of the driving shaft 120 are disposed outside the casing 110, respectively.

Specifically, the drive shaft 120 includes a shaft portion 121 and a pin portion 122 . The shaft portion 121 is coupled to the clutch assembly 2, and the pin portion 122 extends from the shaft portion 121 and is coupled to the orbiting scroll 130 with an eccentric bush 125 interposed therebetween. Accordingly, the driving force transmitted through the clutch assembly 2 is transmitted to the orbiting scroll 130 through the driving shaft 120 .

The orbiting scroll 130 according to the present embodiment is coupled to the rear end of the driving shaft 120 with the eccentric bush 125 interposed therebetween and supported by the frame portion 1122 of the front housing 112 in the axial direction. Accordingly, the orbiting scroll 130 receives rotational force through the driving shaft 120 while being supported in the axial direction by the frame portion 1122 of the front housing 112 and performs a orbital motion.

Specifically, the orbiting scroll 130 includes an orbiting mirror plate part 131, an orbiting wrap 132, and a driving shaft coupling part 133. The orbiting scroll 130 may be formed of a material lighter than the front housing 112, for example aluminum. Accordingly, it is possible to increase compressor efficiency by reducing the load on the balance weight.

The turning mirror plate 131 is formed in a disk shape. An orbiting wrap 132 forming a compression chamber V is formed on one side (rear surface) of the orbiting mirror plate unit 131 by being engaged with a fixing wrap 142 to be described later, and the other side (front surface) of the orbiting mirror plate unit 131 is formed. side) is formed with a drive shaft coupling portion 133 to which the eccentric bush 125 is coupled to receive rotational force through the drive shaft 120. Accordingly, the rear surface of the turning head plate part 131 forms the compression chamber V together with the front face of the fixed head plate part 141 to be described later, while the front face of the turning head plate part 131 forms the front housing 112 It is supported in the axial direction on the scroll support surface 1122b of the to form an axial bearing surface.

A thrust plate 135 may be provided between the rear surface of the turning head plate unit 131 and the scroll support surface 1122b. However, when the front housing 112 and the orbiting scroll 130 constituting the axial bearing surface are made of different materials, the thrust plate 135 described above may be excluded. However, in this embodiment, the front housing 112 and the orbiting scroll 130 will be described based on an example in which a thrust plate 135 is provided between the front housing 112 and the orbiting scroll 130 even though they are made of different materials.

The thrust plate 135 may be formed of a material different from that of the orbiting scroll 130 or/and the front housing 112 . For example, the front housing 112 may be formed of cast iron, the orbiting scroll 130 may be formed of aluminum, and the thrust plate 135 may be formed of a steel plate having greater stiffness than the front housing 112 and/or the orbiting scroll 130. can Accordingly, it is possible to more effectively lubricate between the orbiting scroll 130 and the front housing 112 .

The thrust plate 135 is formed in an annular shape. For example, the thrust plate 135 is formed in substantially the same shape as the scroll support surface 1122b of the front housing 112 . A pin hole 1351 is formed in the thrust plate 135 to insert the anti-rotation pin 171 therein. The pin holes 1351 are formed at predetermined intervals along the circumferential direction to correspond to the anti-rotation pins 171 . Accordingly, the thrust plate 135 may be coupled to the scroll support surface 1122b of the front housing 112 by the anti-rotation pin 171 .

A ring insertion groove 1311 is formed on the front surface of the swing mirror plate unit 131 so that the anti-rotation pin 171 constituting a part of the anti-rotation mechanism 170 is pivotably inserted. Accordingly, the rotation prevention ring 172 in which the orbiting scroll 130 receiving the rotational force by the driving shaft 120 is inserted into the ring insertion groove 1311 and the rotation prevention pin 171 inserted into the rotation prevention ring 172 is driven by a turning motion.

The orbiting wrap 132 extends toward the fixed scroll 140 from one side (rear surface) of the orbiting mirror plate 131 . The orbiting wrap 132 may be formed in various shapes such as an involute to correspond to the stationary wrap 143 .

A tip seal groove is formed on the axial end surface of the orbiting wrap 132 into which a tip seal member (not shown) can be inserted. Accordingly, axial leakage between the compression chambers through the axial end face of the orbiting wrap 132 can be suppressed.

The orbiting wrap 132 may extend to an outer circumferential surface of the orbiting head plate unit 131 . Accordingly, it is possible to maximize the suction volume by maximally extending the wrap length of the orbiting wrap 132 .

At the winding direction end of the orbiting wrap 132 and the winding direction end of the stationary wrap 142 to be described later, a first suction end 132a and a second suction end ( 142a) may be formed respectively. This will be described later together with the fixing wrap 142 .

The driving shaft coupling portion 133 extends from the geometric center of the orbiting scroll 130 toward the front housing 112 . The drive shaft coupling portion 133 is formed in a cylindrical shape, and a third support bearing 187 may be provided between an inner circumferential surface of the drive shaft coupling portion 133 and an outer circumferential surface of the eccentric bush 125 . As the third support bearing 187, a bush bearing, a ball bearing, or a needle bearing may be applied. In this embodiment, an example in which a needle bearing is applied is shown.

In a state in which the fixed scroll 140 according to the present embodiment is inserted into the main housing 111, the front surface thereof is axially supported and fixed to the front housing 112 and the rear surface to the rear housing 113, respectively. Accordingly, the inner space of the casing 110 is separated into a suction space 110a accommodating the orbiting scroll 130 around the fixed scroll 140 and a discharge space 110b including a part of the fixed scroll 140, , The orbiting scroll 130 forms two pairs of compression chambers while performing a orbital motion with respect to the fixed scroll 140.

Specifically, the fixed scroll 140 includes a fixed end plate 141 and a fixed wrap 142 .

The fixed end plate 141 is formed in a disk shape. The outer circumferential surface of the fixed end plate portion 141 may be inserted in contact with the inner circumferential surface of the casing 110, that is, the inner circumferential surface of the main housing 111. A third sealing member 183 may be inserted into the outer circumferential surface of the fixed end plate 141 . Accordingly, the outer circumferential surface of the fixed head plate 141 and the inner circumferential surface of the main housing 111 are tightly sealed, so that the inner space of the casing 110 is formed between the suction space (and oil storage space) 110a on the front side and the discharge space on the rear side. It can be separated by space (110b).

Although not shown in the drawings, when the previously described sealing protrusion (not shown) is formed on the rear housing 113, a third sealing member (not shown) is formed between the inner circumferential surface of the sealing protrusion and the outer circumferential surface of the fixed head plate 141 facing the sealing protrusion. ) may be inserted.

A discharge port 1411 is formed in the center of the fixed end plate 141 . One outlet 1411 may be formed to communicate with both compression chambers (V), or a plurality may be formed to communicate with both compression chambers (V) independently. In this embodiment, an example in which one discharge port 1411 is formed is disclosed.

At least one or more bypass holes 1412a and 1412b may be formed around the outlet 1411 . The bypass holes 1412a and 1412b include a bypass hole for preventing overcompression (hereinafter, a first bypass hole) 1412a for suppressing overcompression and/or a bypass hole for capacity variation for capacity variation (hereinafter, a second bypass hole). pass hole) 1412b may be formed. The first bypass hole 1412a is formed independently for each compression chamber V in the vicinity of the discharge port 1411, and the second bypass hole 1412b is more than the discharge port 1411 than the first bypass hole 1412a. ) It can be formed independently for each compression chamber at a location farther from.

In other words, the discharge port 1411 is a hole through which the refrigerant compressed in the compression chamber V is discharged to the discharge chamber 110b, and communicates between the final compression chamber and the discharge space 110b. The first bypass hole 1412a is a hole for discharging the refrigerant compressed in the first intermediate compression chamber located near the outlet 1411 in advance, and the first intermediate compression chamber around the outlet 1411 and the discharge space 110b communicate between The second bypass hole 1412b is a hole for discharging the refrigerant compressed in the second intermediate compression chamber located near the suction end and far from the discharge port 1411 to the discharge space 110b in advance, and is located in the second middle around the suction end. Communication is provided between the compression chamber and the discharge space 110b.

Since these discharge ports 1411 as well as the first bypass hole 1412a and the second bypass hole 1412b are all holes for discharging the refrigerant in the compression chamber V to the discharge space 110b, hereinafter, the discharge port 1411 ) can be described as the first discharge port, the first bypass hole 1412a as the second discharge port, and the second bypass hole 1412b as the third discharge port. Accordingly, the discharge valve to be described later can be described as a first discharge valve, the first bypass valve as a second discharge valve, and the second bypass valve 147 as a third discharge valve.

The discharge port 1411, the first bypass hole 1412a, and the second bypass hole 1412b are opened and closed by corresponding valves, respectively. For example, the outlet 1411 is opened and closed by the discharge valve, the first bypass hole 1412a is opened and closed by the first bypass valve, and the second bypass hole 1412b is opened and closed by the second bypass valve 147. do.

The discharge valve and the first bypass valve may be formed independently or may be connected to each other and formed as a single body. This embodiment shows an example in which the discharge valve and the first bypass valve are formed as a single body. Hereinafter, the discharge valve ( ) and the first bypass valve are bundled and defined as the discharge valve member 192 and described.

For example, the discharge valve member 192 may be formed by being separated from one valve fixing end 1921 into a plurality of valve parts 1922a and 1922b. The valve fixing end 1921 is fixed to the fixed head plate 141 by a valve support member (hereinafter, used together with a retainer) 193 to be described later, and the plurality of opening/closing parts 1922a and 1922b are discharge ports that are the first discharge ports. The first valve unit 1922a that opens and closes the valve 1411 and the second valve unit 1922b that opens and closes the first bypass hole 1412a, which is the second discharge port, may extend as a unit from the valve fixing end 1921. . Accordingly, the space for installing the discharge valve and the first bypass valve in the fixed head plate 141 is reduced, and at the same time, the discharge valve and the first bypass valve are collectively assembled, thereby reducing assembly man-hours. The discharge valve member 192 will be described later along with the retainer 193.

Meanwhile, a discharge space 110b is formed between the rear surface of the fixed head plate 141 and the inner space of the rear housing 113 facing the same, and the discharge space 110b is formed between the first discharge space 110b1 and the second discharge space 110b. It can be separated by the discharge space (110b2). For example, a partition protrusion 1413 extending toward the rear housing 113 by a predetermined height may be formed on the rear surface of the fixed head plate portion 141 .

The partition protrusion 1413 is formed in a substantially V-shaped ring shape when projected in an axial direction to separate the first discharge space 110b1 and the second discharge space 110b2. For example, a first discharge space 110b1 may be formed outside the partition protrusion 1413 and a second discharge space 110b2 may be formed inside the partition protrusion 1413 .

The first discharge space 110b1 may communicate with the refrigerant discharge port 1131 described above, and the second discharge space 110b2 may communicate with the bypass port 1132 described above. The discharge valve 145 and the first bypass valve 146 belong to the first discharge space 110b1, and the second bypass valve 147 belongs to the second discharge space 110b2. Accordingly, in the first discharge space 110b1, the refrigerant discharged from the discharge pressure chambers (unsigned) of both compression chambers (V) or bypassed from the first intermediate pressure chamber (unmarked) of both compression chambers (V) will be described later. Through the refrigerant discharge pipe 116, it forms a substantial discharge space that guides the condenser 20 of the refrigeration cycle, and the second discharge space 110b2 is an intermediate pressure chamber of both compression chambers (the second intermediate pressure lower than the first intermediate pressure chamber). A kind of bypass space is formed in which the refrigerant bypassed in the pressure chamber is recovered to the suction space 110a of the casing 110 through the refrigerant recovery pipe 151 to be described later.

The partition protrusion 1413 may be formed only on the fixed head plate portion 141, but may also be formed on the front surface of the rear housing 113 facing the fixed head plate portion 141 in some cases. For example, a first partitioning protrusion (for convenience, reference numerals of the partitioning protrusion) 1141 are on the rear surface of the fixed head plate 141, and a second partitioning protrusion 1133 is on the front surface of the rear housing 113. They may be formed to correspond to each other. In this case, the refrigerant discharge port 1131 may be formed outside the second partition protrusion 1133 and the bypass port 1132 may be positioned inside the second partition protrusion 1133, respectively.

A bypass guide groove 1413a is formed inside the partition protrusion 1413. The bypass guide groove 1413a is formed in a substantially V-shape to accommodate the second bypass holes 1412b and 1412b of both compression chambers V together. When the partition protrusion is divided into the first partition protrusion 1413 and the second partition protrusion 1133, the bypass guide groove may be formed in the first partition protrusion 1413 and the second partition protrusion 1133, respectively. It may be formed only on one partition protrusion.

Outside the partition protrusion 1413, a first discharge port forming the aforementioned discharge port 1411 and a second discharge port forming the first bypass hole 1412a are formed. Since the first discharge port forms a substantial discharge port 1411, it is formed larger than the second discharge port.

The discharge port 1411 communicates with the final compression chamber and is formed at the center of the fixed end plate 141, and the first bypass hole 1412a communicates with the first intermediate compression chamber and is formed around the discharge port 1411. One discharge port 1411 is formed, and one or a plurality of first bypass holes 1412a are formed on both left and right sides of the discharge port 1411 . For convenience, this embodiment shows an example in which each of the first bypass holes 1412a is formed one by one.

Around the outlet 1411 and the first bypass hole 1412a, a valve mounting portion 191, which will be described later, is recessed to a predetermined depth. Then, the head plate thickness (hereinafter referred to as inner head plate thickness) t2 within the valve mounting portion 191 becomes smaller than the head plate thickness outside the valve mounting portion 191 (hereinafter referred to as the outer head plate thickness t1). Accordingly, the inner head plate thickness ( As the discharge length L1 of the same discharge port 1411 and the first bypass hole 1412a as t2 is shorter than the outer plate thickness t1, the dead volume at the discharge port 1411 and the first bypass hole 1412a is can be reduced (see Fig. 6).

In addition, a retainer fixing groove 1911 to be described later is recessed and formed in the valve mounting portion 191 by a predetermined fixing depth D1. The fixing depth D1 of the retainer fixing groove 1911 is formed to be smaller than the receiving depth D2 of the valve receiving groove 1912 to be described later. Accordingly, the fastening depth D3 of the fastening bolt 195 fastening the retainer 193 can be secured. (See Fig. 9)

The fixed wrap 142 extends toward the orbiting scroll 130 from one side (front surface) of the fixed end plate 141 . The stationary wrap 142 may be formed in various shapes such as an involute to correspond to the orbiting wrap 132 .

A tip seal groove is formed on an axial end surface of the fixing wrap 142 into which a tip seal member (not shown) can be inserted. Accordingly, axial leakage between the compression chambers through the axial end face of the fixing wrap 142 can be suppressed.

Like the orbiting wrap 132, the stationary wrap 142 may extend to the outer circumferential surface of the stationary head plate portion 141. Accordingly, it is possible to maximize the suction volume by maximally extending the wrap length of the fixing wrap 142 .

The stationary wrap 142 is disposed so that the end in the winding direction is out of phase with the end of the orbiting wrap 132 in the winding direction by approximately 180°. For example, a first suction end 132a, which will be described later, is formed at an outer end of the orbiting wrap 132, and a second suction end 142a is formed at an outer end of the stationary wrap 142, respectively. Accordingly, the stationary wrap 142 together with the orbiting wrap 132 forms a so-called symmetric compression chamber.

Reference numeral 126, which is not described in the figure, is a main balance weight.

The scroll compressor according to the present embodiment as described above operates as follows.

That is, when operation of the gas engine heat pump 1 is selected, the clutch assembly 2 transmits driving force to the driving shaft 120 . The driving force transmitted to the drive shaft 120 is transmitted to the orbiting scroll 130 through the drive shaft 120 .

Then, in a state where the orbiting scroll 130 is supported by the front housing 112, it orbits as much as the eccentric distance of the eccentric bush 125, and at the same time, a suction chamber is placed between the orbiting wrap 132 and the stationary wrap 142. , an intermediate pressure chamber, and two pairs of compression chambers (V) consisting of a discharge chamber are formed in succession. The volume of the compression chamber (V) is reduced while moving toward the center by the continuous turning motion of the orbiting scroll (130), and the refrigerant is compressed while moving along the compression chamber (V) to form the first discharge port (1411). It is discharged through the discharge space 110b, more precisely, into the first discharge space 110b1.

At this time, the refrigerant in the compression chamber (V) is compressed to a set pressure while moving from the intermediate pressure chamber to the discharge pressure chamber. may rise above the pressure. Then, part of the refrigerant moving from the intermediate pressure chamber to the discharge pressure chamber passes through the first bypass hole 1412a constituting the second discharge port before reaching the discharge pressure chamber, from each compression chamber V to the discharge space 110b, to be precise. It is bypassed in advance to the first discharge space 110b1. Through this, it is possible to suppress the refrigerant from being overcompressed to a set pressure or higher in both compression chambers (V), thereby increasing compressor efficiency and ensuring stability of the orbiting wrap 132 and the stationary wrap 142 constituting the compression unit.

On the other hand, in the case where the discharge valve and the first bypass valve constituting the discharge valve member are each made of reed type valves as described above, the corresponding discharge port and the first bypass hole become a dead volume, and compression efficiency may decrease.

Therefore, in this embodiment, the discharge length of the discharge port and the first bypass hole can be reduced in the fixed end plate serving as a valve plate, thereby reducing the dead volume in the discharge port and the first bypass hole. At the same time, the reliability of the discharge valve assembly can be increased by ensuring fastening strength of the retainer supporting the discharge valve and the first bypass valve.

3 is an exploded perspective view of the discharge valve assembly according to the present embodiment, FIG. 4 is a perspective view showing an assembled discharge valve member in FIG. 3, and FIGS. 5A and 5B are an embodiment of the valve mounting portion in FIG. These are schematic diagrams showing examples, and FIG. 6 is a top plan view of the fixed scroll in FIG. 3, FIG. 7 is a cross-sectional view of “IX-IX” in FIG. 6, and FIG. 8 is a cross-sectional view of “X-X” of FIG. , FIG. 9 is a cross-sectional view "XI-XI" of FIG.

Referring to FIGS. 3 to 9 , the fixed scroll 140 according to the present embodiment includes a fixed head plate 141 and a fixed wrap 142 as described above. The fixed head plate portion 141 is formed in a disk shape having a preset head plate thickness (or outer head plate thickness) t1, and the fixed wrap 142 has a preset wrap thickness on one side of the fixed head plate portion 141. It is formed into a spiral with

A partition protrusion 1413 is formed on the rear surface of the fixed head plate 141, a discharge port 1411 and a first bypass hole are formed on the outside of the partition protrusion 1413, and a second bypass is formed on the inside of the partition protrusion 1413. Holes 1412b are formed respectively. The discharge port 1411 is formed at the center (Of) of the fixed end plate 141, and one or a plurality of first bypass holes are formed on both left and right sides of the discharge port 1411, respectively.

The discharge port 1411 and the first bypass hole 1412a are formed to be accommodated in the valve mounting portion 191 constituting a part of the discharge valve assembly 190 . For example, the discharge port 1411 and the first bypass hole 1412a pass through the fixed end plate 141 in the axial direction, but are formed to be accommodated in the valve receiving groove 1912 of the valve mounting portion 191. Accordingly, the discharge length L1 of the discharge port 1411 and the discharge length L1 of the first bypass hole 1412a are equal to each other, and these discharge lengths L1 are the head plate outside the valve receiving groove 1912. It may be formed smaller than the thickness, that is, the outer head plate thickness t1 of the fixed head plate portion 141 .

Specifically, the valve mounting portion 191 includes a retainer fixing groove 1911 and a valve receiving groove 1912 . The retainer fixing groove 1911 is a part where a retainer 193 to be described later is inserted and fastened, and the valve receiving groove 1912 is a discharge valve member 192 to be described later inserted into the discharge port 1411 and the first pass hole 1412a. ) is the part that opens and closes.

The retainer fixing groove 1911 is formed on both sides in the circumferential direction or the width direction with the first accommodating portion 1912a of the valve receiving groove 1912 to be described later interposed therebetween, and the retainer fixing portion of the retainer 193 to be described later ( 1931) may be formed to correspond to the shape. For example, the retainer fixing groove 1911 may be formed stepwise in a substantially square groove shape on the rear surface of the fixing head plate portion 141 . Accordingly, the retainer fixing part 1931 is inserted into the retainer fixing groove 1911 and constrained in the lateral direction, so that the retainer fixing part 1931 can be temporarily assembled to the retainer fixing groove 1911 when the retainer 193 is assembled. Through this, the retainer can be easily assembled.

The fixing depth D1 of the retainer fixing groove 1911 is smaller than the receiving depth D2 of the valve receiving groove 1912 . Accordingly, when the retainer fixing part 1931 inserted into the retainer fixing groove 1911 is fastened with the fastening bolt, the fastening depth D3 of the fastening bolt 195 can be secured.

A bolt fastening groove 1911a is formed in the retainer fixing groove 1911. A plurality of bolt fastening grooves 1911a may be formed in both retainer fixing grooves 1911, respectively. For example, two bolt fastening grooves 1911a may be formed in the left retainer fixing groove 1911' and two in the right retainer fixing groove 1911".

Both bolt fastening grooves 1911a may be disposed symmetrically left and right around the first accommodating portion 1912a of the valve accommodating groove 1912 to be described later. For example, both bolt fastening grooves 1911a may be disposed parallel to each other and formed at equal intervals along the radial direction. In this case, while some of the bolt fastening grooves 1911a overlap with the fixed wrap 142 in the axial direction, some of the bolt fastening grooves 1911a may not overlap with the fixed wrap 142 in the axial direction. As described above, when the bolt fastening grooves 1911a are arranged symmetrically, not only is it easy to process the bolt fastening grooves 1911a, but also the retainer ( 193) can increase the reliability of coupling.

In addition, both bolt fastening grooves 1911a may be disposed asymmetrically left and right around the first accommodating portion 1912a of the valve accommodating groove 1912 to be described later. For example, the bolt fastening grooves 1911a may be arranged parallel to each other at different intervals along the radial direction. In this case, all bolt fastening grooves 1911a may be arranged to overlap with the fixing wrap 142 in the axial direction. As described above, when the bolt fastening grooves 1911a are asymmetrically arranged, all bolt fastening grooves 1911a overlap with the fixing wrap 142 in the axial direction, so that the fastening load of the fastening bolts 195 can be more effectively distributed. there is. Accordingly, even if a more deeply recessed valve receiving groove 1912 is formed around the retainer fixing groove 1911a, deformation of the fixed head plate portion 141 due to bolt fastening can be effectively suppressed.

Although not shown in the drawing, the retainer fixing groove 1911 may not be formed on the rear surface of the fixing head plate 141 . Even in this case, a bolt fastening groove 1911a is formed in the fixed head plate part 141 at the corresponding position, so that the retainer fixing part 1931, which will be described later, can be fastened with bolts while resting on the rear surface of the fixed head plate part 141.

Both sides of the bolt fastening grooves 1911a may be arranged parallel to each other, or the intervals between the bolt fastening grooves 1911a may be differently arranged. For example, the distance between the bolt fastening grooves 1911a' located on the inside of both bolt fastening grooves 1911a is called the inner gap G1, and the distance between the bolt fastening grooves 1911a "located on the outside is the outer gap ( G2), the outer gap G2 may be formed larger than the inner gap G1. Accordingly, the fastening force of the fastening bolt 195 fastened to both bolt fastening grooves 1911a can be further strengthened. Through this, the retainer 193 can be stably fixed to the fixed scroll while applying the relatively small fastening bolt 195.

Referring to FIG. 6, the valve receiving groove 1912 is recessed into the rear surface of the fixed head plate part 141 by a predetermined depth, but extends by a predetermined length in the radial direction from the center (Of) of the fixed head plate part 141. For example, the valve accommodating groove 1912 is the first accommodating part 1912a in which the valve fixing end 1921 of the discharge valve member 192 is accommodated and the valve opening/closing end 1922 of the discharge valve member 192. ) may include a second accommodating portion 1912b accommodating therein. Accordingly, the first accommodating portion 1912a is attached to the valve fixing end 1921 of the discharge valve member 192, and the second accommodating portion 1912b is It may be formed to correspond to the valve opening/closing ends 1922 of the discharge valve member 192, respectively.

The first accommodating part 1912a and the second accommodating part 1912b may be continuously formed. For example, the second accommodating portion 1912b may be formed to extend from the end of the first accommodating portion 1912a toward the center Of of the fixed head plate 141 and extend to both left and right sides. In other words, the first accommodating portion 1912a may have a long rectangular shape in the radial direction, whereas the second accommodating portion 1912b may have a long rectangular shape in the circumferential direction (left-right direction or width direction).

The first accommodating portion 1912a and the second accommodating portion 1912b may be formed to have the same depth. Accordingly, not only can the valve receiving groove 1912 be formed easily, but also the reliability of the discharge valve member 192 can be increased by reducing processing errors of the valve receiving groove 1912. However, in some cases, the depth of the first accommodating portion 1912a may be formed to be slightly shallower than the depth of the second accommodating portion 1912b. In this case, the valve opening/closing end 1922 of the discharge valve member 192, which will be described later, is minutely separated from the valve seat surface of the discharge port 1411 and the first bypass hole 1412a, thereby increasing the opening speed of the valve.

As described above, the first accommodating portion 1912a is formed in a long groove shape in the radial direction, and a fixing pin portion protrudes in the axial direction toward the retainer 193 on the outer side far from the center (Of) of the fixing head plate portion 141 (1913) can be formed. In other words, the fixing pin part 1913 extends in the axial direction toward the valve fixing hole 1921a of the discharge valve member 192 in the first accommodating part 1912a, and the fixing pin part 1913 is a discharge valve member 192 to be described later. ) can be inserted into the valve fixing hole 1921a to support the valve fixing end 1921 of the discharge valve member 192.

It is preferable that at least two fixing pins 1913 are formed to stably support the discharge valve member 192 . For example, two fixing pins 1913 may be provided, spaced apart from each other by a predetermined interval in a direction from the first accommodating part 1912a of the valve accommodating groove 1912 toward the second accommodating part 1912b. . Accordingly, while minimizing the width of the valve fixing end 1921 of the discharge valve member 192, a wide gap in the width direction between the valve fixing hole 1921a and the valve fixing end 1921 is secured, resulting in a discharge valve member due to repeated opening and closing operations. (192) damage can be suppressed.

Also, the fixing pin part 1913 may be formed to be positioned on a first center line CL1 extending in a radial direction from the center of the discharge port 1411 . Accordingly, even if the first opening/closing portion 1922a of the discharge valve member 192 that opens and closes the discharge port 1411 receives a stronger discharge load than the second opening/closing portion 1922b, the discharge load is evenly transferred to the valve fixing end 1921. Accordingly, the reliability of the valve can be secured.

As described above, the second accommodating portion 1912b according to the present embodiment may be formed in a long rectangular shape in the circumferential direction (left-right direction or width direction). However, the second accommodating portion 1912b may be formed in various ways according to the arrangement of the discharge port 1411 and the first bypass hole 1412a. For example, when the discharge port 1411 and both first bypass holes 1412a are disposed on a straight line, the second accommodating portion 1912b may be formed in a rectangular shape, but the discharge port 1411 and both first bypass holes 1412a may be formed in a rectangular shape. When the hole 1412a is disposed in an arc shape, the second accommodating portion 1912b may also be formed in an arc shape to correspond thereto.

The second accommodating portion 1912b may be formed to independently correspond to the single outlet 1411 and the plurality of first bypass holes 1412a. However, the discharge port 1411 and the first bypass hole 1412a may be formed in one second accommodating part 1912b. In other words, one second accommodating part 1912b is formed in the fixed head plate 141, and one discharge port 1411 and a plurality of first bypass holes 1412a are formed in the one second accommodating part 1912b. can be formed together. Accordingly, the manufacturing cost may be reduced by simplifying the processing of the second accommodating portion 1912b.

The second accommodating portion 1912b may be formed to have substantially the same depth as the first accommodating portion 1912a. In other words, the valve receiving groove 1912 may be formed with the same depth as a whole. Accordingly, the head plate thickness (inner head plate thickness) t2 of the fixed head plate portion 141 inside the valve receiving groove 1912 is the head plate thickness (outer head plate thickness) of the fixed head plate portion 141 outside the valve receiving groove 1912. (t1) may be formed as thin as about 1/3.

For example, when the outer head plate thickness t1 is approximately 11.5 mm, the inner head plate thickness t2 may be approximately 3.5 mm. Then, the length of the discharge port 1411 and the length of the first bypass hole 1412a equal to the thickness of the inner head plate are the same as the discharge port 1411 and the first bypass in the conventional fixed head plate 141 without the valve receiving groove 1912. It may be approximately 1/3 of the discharge length L1 of the pass hole 1412a. Then, the dead volume in the discharge port 1411 and the first bypass hole 1412a is reduced by that much, so compression efficiency can be improved.

The discharge valve member 192 according to the present embodiment is inserted into the valve receiving groove 1912 provided on the rear surface of the fixed head plate 141 to form the first discharge port 1411, the discharge port 1411 and the second discharge port 1411 ) to open and close the first bypass hole 1412a.

In the discharge valve member 192, the discharge valve opening and closing the discharge port 1411 and the bypass valve opening and closing the first bypass hole 1412a may be formed as a single body or may be formed independently of each other. The present embodiment is described focusing on an example in which the discharge valve and the first bypass valve are formed as a single body, but even when the discharge valve and the first bypass valve are formed independently, the valve receiving groove 1912 and the discharge valve member 192 ) and the basic configuration of the retainer 193, which will be described later, and the operational effect thereof may be substantially the same.

Specifically, the discharge valve member 192 according to the present embodiment includes a valve fixing end 1921 and a valve opening/closing end 1922. The valve fixing end 1921 forms one end of the discharge valve member 192 and is inserted into the first accommodating portion 1912a of the valve receiving groove 1912, and the valve opening/closing end 1922 forms the other end of the discharge valve member 192. and is inserted into the second accommodating portion 1912b of the valve accommodating groove 1912. Accordingly, the discharge valve member 192 may be inserted into the valve receiving groove 1912 and supported by a retainer 193 to be described later.

The valve fixing end 1921 is formed long in the radial direction to correspond to the first accommodating portion 1912a of the valve accommodating groove 1912. In other words, the valve fixing end 1921 is formed of a flat plate body, and has a radial length longer than a width length. Accordingly, the valve fixing end 1921 may be formed in a rectangular shape having approximately the same width in the radial direction.

A valve fixing hole 1921a is formed at the outer end of the valve fixing end 1921. Two valve fixing holes 1921a are formed at a predetermined interval, and arranged at a predetermined interval in the radial direction so that the fixing pin portion 1913 of the valve receiving groove 1912 described above passes through. Accordingly, a plurality of valve fixing holes 1921a may be formed without increasing the width of the valve fixing end 1921 . Through this, even if the valve opening/closing end 1922 is opened and closed while bending around the valve fixing end 1921, damage to the valve fixing end 1921 due to stress concentration can be suppressed.

The valve opening/closing end 1922 is formed as a flat plate body like the valve fixing end 1921 and extends from the valve fixing end as a single body. Accordingly, the discharge valve member 192 can be easily manufactured, and reliability can be improved by suppressing concentration of stress even in repetitive opening and closing operations for a long period of time.

Specifically, the valve opening/closing end 1922 includes a first valve part 1922a and a second valve part 1922b. The first valve part 1922a is a part that opens and closes the outlet 1411, and the second valve part 1922b is a part that opens and closes the first bypass hole 1412a. Accordingly, the first valve unit 1922a is located in the center, and the second valve units 1922b are located on both left and right sides of the first valve unit 1922a.

The first valve unit 1922a is formed to be positioned on the same line as the valve fixing end 1921 in the radial direction. Accordingly, as the first valve unit 1922a is primarily supported by the valve fixing end 1921, the first valve unit 1922a is stably supported even if it receives a relatively larger discharge load than the second valve unit 1922b. It can be.

The second valve unit 1922b may be formed parallel to the first valve unit 1922a on both sides of the first valve unit 1922a. In this case, a plurality of connection parts 1923 extending in the circumferential direction are formed on both sides of the second valve part 1922b, and the second valve part 1922b is connected to each first bypass at both connection parts 1923. Each may be formed to extend in a radial direction toward the hole 1412a. Accordingly, the second valve unit 1922b may be formed in a trident shape together with the first valve unit 1922a.

The second valve unit 1922b may have the same thickness as the first valve unit 1922a, but may be smaller than the first valve unit 1922a. In other words, as the inner diameter of the first bypass hole 1412a is smaller than the inner diameter of the outlet 1411, the diameter of the second valve unit 1922b may be smaller than that of the first valve unit 1922a. there is. Accordingly, the second valve unit 1922b can quickly open and close the first bypass hole 1412a even when the second support portion of the retainer 193 is shallowly curved or inclined.

The retainer 193 according to this embodiment is inserted into the valve receiving groove 1912 with the discharge valve member 192 interposed therebetween. Accordingly, the retainer 193 can limit the amount of opening of the discharge valve member 192 while the discharge valve member 192 is fixed to the valve receiving groove 1912 .

Specifically, the retainer 193 may include a retainer fixing part 1931 , a valve fixing part 1932 and a valve support part 1933 . The retainer fixing part 1931 is a part to which the retainer 193 is fixed to the fixed head plate part 141, and the valve fixing part 1932 is a part to fix the discharge valve member 192 to the fixed head plate part 141, The valve support part 1933 is a part that limits the opening amount of the discharge valve member 192. The retainer fixing part 1931, the valve fixing part 1932, and the valve support part 1933 may be formed as a single body, or the retainer fixing part 1931 is assembled to the valve fixing part 1932 and the valve support part 1933 and combined. It could be. In this embodiment, the retainer fixing part 1931, the valve fixing part 1932, and the valve support part 1933 are formed as a single body. (1933) will be described later as another embodiment.

The retainer fixing part 1931 is formed of a metal plate. For example, the retainer fixing part 1931 may be formed of the same material as the fixed scroll 140, for example, a cast iron material. Accordingly, the retainer fixing part 1931 can be firmly fastened to the fixed scroll 140 by bolts. However, the retainer fixing part 1931 may be made of aluminum or the like in consideration of weight.

The retainer fixing part 1931 is formed in a substantially rectangular plate shape. As described above, the retainer fixing groove 1911 provided on the rear surface of the fixed head plate portion 141 is formed on both sides in the circumferential direction or width direction with the first accommodating portion 1912a of the valve accommodating groove 1912 interposed therebetween. Therefore, both ends of the retainer fixing part 1931 can cross the first accommodating part 1912a of the valve accommodating groove 1912 and be inserted into both retainer fixing grooves 1911 and fastened with bolts. Accordingly, the retainer fixing parts 1931 can be stably fixed by being inserted into both retainer fixing grooves 1911, respectively.

The retainer fixing part 1931 may be completely inserted into the retainer fixing groove 1911 provided on the rear surface of the fixed end plate 141 . For example, the thickness of the retainer fixing part 1931 may be smaller than or equal to the depth of the retainer fixing groove 1911 . Accordingly, while the retainer fixing part 1931 is inserted into the retainer fixing groove 1911, the retainer fixing part 1931 is not exposed to the outside of the retainer fixing groove 1911. Through this, it is possible to suppress a decrease in the volume of the first discharge space 110b1 due to the retainer 193 .

A bolt hole 1931a is formed through the retainer fixing part 1931. The bolt hole 1931a is formed to correspond to the bolt fastening groove 1911a provided in the retainer fixing groove 1911. Accordingly, the fastening bolt 195 passing through the bolt hole 19131a is fastened to the bolt fastening groove 1911a so that the retainer fixing part 1931 can be fastened to the retainer fastening groove 1911.

Referring to FIG. 8, the inner diameter D4 of the bolt hole 1931a is smaller than the lap thickness t3 of the fixing wrap 142, and the bolt hole 1931a is positioned on the same axis as the fixing wrap 142. can be formed to In other words, at least a portion of the bolt hole 1931a may be formed at a position overlapping the fixing wrap 142 in the axial direction. This is also true of the bolt fastening groove (1911a). Accordingly, the retainer fixing groove 1911 and/or the valve receiving groove 1912 fix the fixing wrap 142 even though the load bearing capacity of the fixing head plate 141 at the position where the fastening bolt 195 is fastened is slightly reduced. It is possible to compensate for the load bearing capacity of the head plate portion 141 . Through this, the retainer 193 can be stably fixed to the fixed scroll 140.

In addition, a plurality of bolt holes 1931a may be formed in both retainer fixing parts 1931, respectively. For example, two bolt fastening grooves 1911a are formed in both retainer fixing grooves 1911, respectively, and two bolt holes 1931a corresponding to the fastening grooves are formed in both retainer fixing parts 1931, respectively. can Accordingly, the retainer 193 may be bolted to the fixed scroll by four fastening bolts.

In addition, a plurality of bolt holes 1931a are formed on both retainer fixing parts 1931, respectively, and these plurality of bolt holes 1931a may be formed at predetermined intervals in the radial direction.

For example, the plurality of bolt holes 1931a located on the left and the plurality of bolt holes 1931a located on the right are each spaced apart by the same interval in the radial direction (exactly, in the longitudinal direction of the retainer) or at different intervals. can be placed and placed. Since the positions of these both bolt holes 1931a should correspond to the previously described bolt fastening grooves 1911a, the description of the bolt fastening grooves 1911a will be substituted for this.

As described above, the valve fixing part 1932 according to the present embodiment may be monolithically extended from the retainer fixing part 1931 . For example, the valve fixing part 1932 has a predetermined height from one side of the retainer fixing part 1931, that is, the lower surface of the retainer fixing part 1931 facing the first accommodating part 1912a of the valve receiving groove 1912. (Thickness) can protrude.

The thickness of the valve fixing part 1932 is shallower than the depth of the first accommodating part 1912a, that is, the thickness of the retainer fixing part 1931 and the thickness of the discharge valve member 192 at the depth of the first accommodating part 1912a. It may be formed equal to or finely larger than the value minus . Accordingly, in a state where the retainer fixing part 1931 is in close contact with the retainer fixing groove 1911, the valve fixing part 1932 is in close contact with the valve fixing end 1921 of the discharge valve member 192 to form the discharge valve member 192. can be stably supported.

A valve fixing surface 1932a supporting the valve fixing end 1921 of the discharge valve member 192 is formed on one side of the valve fixing part 1932, and the discharge valve member 192 is attached to the valve fixing surface 1932a. A pin fixing groove 1932b is formed so that the penetrating fixing pin 1913 is inserted. For example, the pin fixing groove 1932b is formed by being depressed by a predetermined depth in the axial direction in the valve fixing surface 1932a facing the discharge valve member 192.

The pin fixing groove 1932b may be formed to correspond to the previously described fixing pin part 1913 and the valve fixing hole 1921a, respectively. For example, a plurality of pin fixing grooves 1932b may be formed at predetermined intervals along the longitudinal direction (radial direction) of the valve fixing part 1932 . Accordingly, since the fixing pin part 1913 passes through the valve fixing hole 1921a of the discharge valve member 192 and is inserted into the pin fixing groove 1932b of the valve fixing part 1932, the fixing pin part 1913 is the discharge valve member ( 192) can be stably supported.

Although not shown in the drawings, the pin fixing groove 1932b may be formed as a single long groove having a length capable of accommodating a plurality of fixing pin parts 1913. Accordingly, tolerance for the pin fixing groove 1932b can be increased, and manufacturing cost can be reduced accordingly.

As described above, the valve support part 1933 according to this embodiment may be formed as a single body with the retainer fixing part 1931 and the valve fixing part 1932. In other words, in the retainer 193, the retainer fixing part 1931, the valve fixing part 1932, and the valve support part 1933 may be formed as a single body. Accordingly, assembly of the retainer 193 can be simplified and assembly cost can be reduced.

The valve support 1933 may be formed as a single body. For example, even when the discharge valve member 192 is made up of three valve parts 1922a (1922b, 1922b) as in the present embodiment, the valve support part 1933 may be made of one. Accordingly, the valve support 1933 can be easily manufactured.

Although not shown in the drawing, the valve support 1933 may be separated into a plurality of pieces. For example, in the case where the discharge valve member 192 is composed of three valve parts 1922a [(1922b) (1922b)] as in the present embodiment, the valve support part 1933 is each of the valve parts 1922a, [(1922b) ) (1922b)] may be formed by being separated into three valve supports (not shown). Accordingly, the amount of opening can be differentially adjusted according to the condition of each valve unit 1922a [(1922b) (1922b)].

7 and 8, the valve support portion 1933 is a surface facing the discharge valve member 192, that is, a valve support surface 1933a facing the valve opening/closing end 1922 of the discharge valve member 192. It may be curved or inclined. For example, the valve support surface 1933 may be formed to gradually move away from the valve receiving groove 1912 toward the end of the valve support portion 1933 from the valve fixing portion 1932 . Accordingly, the valve opening/closing end 1922 of the discharge valve member 192 may open and close the discharge port 1411 and the first bypass hole 1412a while rotating around the valve fixing part 1932 .

The valve support surfaces 1933a may be formed in the same shape as each other. For example, the valve support surface 1933a may be curved with the same curvature or inclined at the same angle. Accordingly, the valve support surface 1933a can be easily formed.

Referring to FIGS. 4, 7, and 8 , the valve support surface 1933a may be formed differently according to the valve part. For example, the valve support surface 1933a corresponding to the first valve part 1922a is the first support surface 1933b, and the valve support surface 1933a corresponding to the second valve part 1922b is the second support surface ( 1933c), the curvature or inclination angle of the first support surface 1933b and the second support surface may be formed to be different from each other. Specifically, the curvature or inclination angle of the first support surface facing the first valve unit 1922a may be greater than the curvature or inclination angle of the second support surface 1933c facing the second valve unit 1922b. Accordingly, the discharge port 1411 opened and closed by the first valve unit 1922a is opened more quickly and more, so that flow resistance at the discharge port 1411 can be lowered. However, since the second valve part 1922b is shorter than the first valve part 1922a, the curvature or inclination angle of the second support surface 1933c may be greater than the curvature or inclination angle of the first support surface 1933b. . In this case, the first bypass hole 1412a is opened and closed more smoothly, so that overcompression can be effectively suppressed.

As described above, when the discharge valve (first valve part) and the first bypass valve (second valve part) constituting the discharge valve member 192 are reed type valves, these discharge valves and the first bypass valve When it is opened and then closed, a part of the refrigerant may remain in the corresponding outlet 1411 and the first bypass hole 1412a and then flow back into the compression chamber V. In other words, as the discharge port 1411 forming the first discharge port and the first bypass hole 1412a forming the second discharge port form a kind of dead volume, compression efficiency may decrease.

However, as in the present embodiment, as the valve receiving groove 1912 is formed to be recessed by a predetermined depth on the rear surface of the fixed head plate 141 serving as a valve plate, the outlet 1411 and the first bypass hole 1412a ) is shortened. Through this, the volume of the discharge port 1411 and the first bypass hole 1412a is reduced, so that the dead volume is reduced. Then, as the amount of refrigerant flowing back into the compression chamber V decreases, the amount of refrigerant flowing backward into the compression chamber V also decreases, so compression efficiency can be improved.

In addition, as retainer fixing grooves 1911 higher than the valve receiving groove 1912 are formed on both sides of the valve receiving groove 1912, the fastening depth or fastening strength of the fastening bolt 195 fastening the retainer 193 is secured This can increase reliability.

In addition, the retainer 193 supporting the discharge valve member 192 is unified, but as the retainer 193 is fastened with a plurality of fastening bolts 195, the fastening force for the discharge valve member 192 and the retainer 193 is increased. can be raised At the same time, as the bolt 195 is fastened at a position overlapping with the fixed wrap 142 in the axial direction, the fastening load is distributed to suppress deformation of the fixed scroll 140 .

Meanwhile, other embodiments of the discharge valve assembly are as follows.

That is, in the above-described embodiment, the retainer constituting a part of the discharge valve assembly is formed as a single body, but in some cases, the retainer may be formed by cooking a plurality of parts.

FIG. 10 is an exploded perspective view of another embodiment of a discharge valve assembly, FIG. 11 is an assembled plan view of FIG. 10 , and FIG. 12 is a sectional view taken along the line "XII-XII" of FIG. 11 .

Referring to FIGS. 10 to 12 , the discharge valve assembly 190 according to the present embodiment may be similar to the above-described discharge valve assembly 190 in its basic configuration and operational effects. For example, in the discharge valve assembly 190, the valve mounting portion 191 is recessed on the rear surface of the fixed end plate 141 constituting the valve plate, and the valve mounting portion 191 forms the discharge valve and the first bypass valve. A discharge valve member 192 is inserted, and a retainer 193 limiting an opening amount of the discharge valve member 192 may be provided on a rear surface of the discharge valve member 192 .

In this case, a part of the retainer 193 is inserted into the valve receiving groove 1912 constituting a part of the valve mounting portion 191 and is provided to face the discharge valve member 192, while a part of the retainer 193 is the valve mounting portion ( 191) is fastened to the fixed end plate 141 outside the retainer fixing groove 1911 forming a part or the valve mounting portion 191. Accordingly, by reducing the discharge length L1 of the discharge port 1411 and the first bypass hole 1412a, the dead volume in the discharge port 1411 and the first bypass hole 1412a is reduced, and the retainer 193 is fastened. Reliability of coupling between the discharge valve member 192 and the retainer 193 may be increased by securing a fastening depth of the fastening bolt 195 to be fastened.

However, in this embodiment, the retainer 193 may be manufactured as a separate type and then assembled. For example, the retainer 193 includes the retainer fixing part 1931, the valve fixing part 1932, and the valve support part 1933 of the above-described embodiment, but the valve fixing part 1932 and the valve support part 1933 are integral On the other hand, the retainer fixing part 1931 may be manufactured separately and then assembled to the fixed end plate part 141. Hereinafter, the retainer fixing part 1931 of the above-described embodiment is defined as the retainer fixing plate 1935, and the valve fixing part 1932 and the valve support part 1933 of the above-described embodiment are bundled and defined as the valve support plate 1936, respectively.

Specifically, the retainer fixing plate 1935 may be formed of a thin plate body. For example, the retainer fixing plate 1935 may be formed of a steel plate, a cast iron plate, or an aluminum plate metal plate body. However, the retainer fixing plate 1935 is not necessarily limited to a metal plate body. In other words, the retainer fixing plate 1935 may be formed of other materials capable of fastening with bolts or may be formed of a material having higher strength than the valve support plate 1936.

In addition, bolt holes 1935a are formed through the retainer fixing plate 1935 around the corners, as in the embodiment of FIG. 3 described above. The arrangement of the bolt holes 1935a may be the same as in the above-described embodiment.

In addition, a pin insertion hole 1935b may be formed in the retainer fixing plate 1935 so that the other end of the fixing pin part 1913 is inserted. As shown in the drawing, the pin insertion hole 1935b may be formed in plural or may be formed as a single long hole. Instead of the pin insertion hole 1935b, it may be formed as a pin insertion groove. Accordingly, the retainer fixing plate 1935 is coupled to the fixing pin portion 1913 penetrating the valve support plate 1936, so that the retainer fixing plate 1935 can be coupled to the fixed scroll 140 together with the valve support plate 1936. Through this, when the retainer fixing plate 1935 and the valve support plate 1936 are fastened, the retainer fixing plate 1935 can be temporarily assembled to the valve support plate 1936, so that not only can the assembly of the retainer fixing plate 1935 be improved, but also the retainer fixing plate ( 1935) and the valve support plate 1936 can increase the bonding force.

Although not shown in the drawings, a fixing pin portion of the retainer fixing plate 1935 may extend toward a pin through hole 1936b of the valve support plate 1936 to be described later, instead of the pin insertion hole. In this case, not only the assembly property of the retainer fixing plate 1935 can be improved, but also the bonding force between the retainer fixing plate 1935 and the valve support plate 1936 can be increased.

The valve support plate 1936 may be formed as a rectangular plate body so as to extend across the retainer fixing plate 1935. The valve support plate 1936 may be formed thicker than the retainer fixing plate 1935. For example, the valve support plate 1936 may have a thickness substantially similar to the depth of the valve receiving groove 1912 of the fixed head plate 141, including the valve thickness.

Since the valve support plate 1936 does not require fastening with bolts, as described above, a material having lower strength than the retainer fixing plate 1935, such as an engineering plastic material, may be used. Accordingly, the valve support plate 1936 is easy to manufacture and can be made of a lighter material than the retainer fixing plate 1935, so that the weight of the retainer 193 can be reduced accordingly.

On one side surface (upper surface) of the valve support plate 1936, a fixed plate coupling groove 1936a may be formed stepwise so that the retainer fixing plate 1935 is inserted and engaged therewith. For example, the fixing plate coupling groove 1936a may be formed to cross the width direction of the valve support plate 1936. Accordingly, the fixing plate coupling groove 1936a is coupled to the valve support plate 1936 in a cross shape so that the retainer fixing plate 1935 can be supported with respect to the valve support plate 1936 in a radial direction.

The fixing plate coupling groove 1936a may be formed at one end of the valve support plate 1936 stepwise. In this case, the length of the valve support plate 1936 can be minimized. Although not shown in the drawing, the fixing plate coupling groove 1936a may be formed stepwise across the middle of the valve support plate 1936. In this case, both sides of the valve support plate 1936 can be supported in the radial direction by the fixing plate coupling groove 1936a, so that the valve support plate 1936 can be stably supported.

A pin through hole 1936b may be formed at the other end of the valve support plate 1936. As in the above-described embodiment of FIG. 3 , a plurality of pin through-holes 1936b may be formed at predetermined intervals along the longitudinal direction of the valve support plate 1936 or may be formed in a single long hole shape. Accordingly, the fixing pin part 1913 protruding from the second accommodating part 1912b of the valve accommodating groove 1912 is the valve fixing hole 1921a of the discharge valve member 192 and the pin through hole 1936b of the valve support plate 1936 ) and is inserted into the pin insertion hole 1935b of the retainer fixing plate 1935, thereby stably supporting the discharge valve member 192.

As described above, when the retainer 193 is separated into the retainer fixing plate 1935 and the valve support plate 1936 and then assembled, the retainer fixing plate 1935 is a metal plate and the valve support plate 1936 is a lighter material than the retainer fixing plate 1935. It is possible to reduce the weight of the retainer 193 while stably fixing the retainer 193. Through this, the weight of the scroll compressor according to the present embodiment can be reduced.

On the other hand, in the above embodiments, the discharge valve member 192 has been described with a focus on an example having a plurality of valve parts 1922a and 1922b, but in some cases, the discharge valve member 192 has one valve part ( not shown). In this case, the valve mounting portion 191, the discharge valve member 192, and the retainer 193 constituting the discharge valve assembly 190 are coupled to the fixed head plate 141 serving as the valve plate, and the discharge valve assembly 190 ) Since the basic configuration and the resulting operation and effect are almost the same as those of the above-described embodiment, the detailed description thereof is replaced by the description of the above-described embodiments.

Further, in the foregoing embodiments, an example in which the discharge valve assembly 190 is applied to the discharge valve and/or the first bypass valve of the scroll compressor has been described, but it is not necessarily applied only to the scroll compressor. For example, the discharge valve assembly 190 according to the present embodiment may be equally applied to a discharge valve assembly of a rotary compressor or a reciprocating compressor. In these cases, at least one discharge port is formed in the valve plate (not shown), and retainer fixing grooves 1911 for fixing the retainer 193 are formed on both sides of the valve receiving groove 1912 including the discharge port in the circumferential direction, respectively. It can be. Even in this case, the valve receiving groove 1912 is formed deeper than the retainer fixing groove 1911 to reduce the discharge length L1 of the discharge port. Through this, the dead volume at the discharge port can be lowered, and at the same time, the coupling force of the discharge valve assembly 190 can be increased by securing the fastening depth D3 to the retainer 193. Since the retainer fixing groove, the valve receiving groove, and the retainer are the same as in the foregoing embodiments, detailed descriptions thereof are replaced with those in the foregoing embodiments.

2: clutch assembly 110: casing
110a: suction space 110b: discharge space
110b1: first discharge space 110b2: second discharge space
111: main housing 111a: first housing protrusion
111b: second housing protrusion 1111: refrigerant suction port
1112: return port 1112a: first return port
1112b: second return port 112: front housing
1121: cover part 1121a: cover protrusion
1121b: shaft accommodating portion 1121b1: front side shaft accommodating portion
1121b2: rear side bearing part 1121c: lubrication space part
1122: frame part 1122a: turning space part
1122b: scroll support surface 113: rear housing
113a: third housing protrusion 1131: discharge port
1132: bypass port 1133: second compartment protrusion
115: refrigerant suction pipe 116: refrigerant discharge pipe
120: drive shaft 121: shaft
122: pin part 125: eccentric bush
1251: sub balance weight 130: orbiting scroll
131: turning head plate 1311: ring insertion groove
132: turning wrap 1321: tip thread member
133: drive shaft coupling part 135: thrust plate
1351: pin hole 140: fixed scroll
141: fixed end plate 1411: discharge port
1412a: first bypass hole 1412b: second bypass hole
1413: compartment protrusion (first compartment protrusion) 1413a: bypass guide groove
142: fixed wrap 147: second bypass valve
151: refrigerant recovery pipe 170: anti-rotation mechanism
171: anti-rotation pin 172: anti-rotation ring
181: first sealing member 182: second sealing member
183: third sealing member 184: shaft sealing member
185: first support bearing 186: second support bearing
187: third support bearing 190: discharge valve assembly
191: valve mounting portion 1911: retainer fixing groove
1911': left retainer fixing groove 1911": right retainer fixing groove
1911a: bolt fastening groove 1911a': inner bolt fastening groove
1911a": outer bolt fastening groove 1912: valve receiving groove
1912a: first accommodating part 1912b: second accommodating part
1913: fixing pin part 192: discharge valve member
1921: valve fixing end 1921a: valve fixing hole
1922: valve opening/closing end 1922a: first valve part
1922b: second valve unit 193: retainer
1931: retainer fixing part 1931a: bolt hole
1932: valve fixing part 1932a: valve fixing surface
1932b: pin insertion groove 1933: valve support
1933a: valve support surface 1933b: first support surface
1933c: second support surface 1935: retainer fixing plate
1935a: bolt fastening hole 1935b: pin fixing hole
1936: valve support plate 1936a: fixed plate coupling groove
1936b: pin fixing hole 195: fastening bolt
CL1: 1st center line D1: fixed depth
D2: Accommodating depth D3: Fastening depth
D4: Inner diameter of bolt hole G1: Inner spacing
G2: outer spacing L1: discharge length
t1: outer head plate thickness t2: inner head plate thickness
t3: lap thickness Of: center of fixed scroll
V: compression chamber V1: first compression chamber
V2: Second compression chamber

Claims (18)

casing;
an orbiting scroll provided with an orbiting wrap and performing a orbital movement inside the casing;
a fixed scroll having a fixed wrap engaged with the orbiting wrap to form a compression chamber and having a discharge port formed to discharge the refrigerant compressed in the compression chamber;
a valve member having one end fixed to the fixed scroll and the other end opening and closing the discharge port; and
A retainer provided on a rear surface of the valve member and fixed to the fixed scroll,
A valve receiving groove into which a part of the retainer is inserted together with the valve member is formed on the rear surface of the fixed scroll facing the retainer,
The retainer,
a retainer fixing part fastened to the fixed scroll;
a valve fixing part extending from the retainer fixing part and being inserted into the valve receiving groove to fix the valve member; and
A valve support portion extending from the valve fixing portion, inserted into the valve receiving groove, and detachable from the valve member to limit the opening amount of the valve member,
The retainer fixing part,
Compressor fastened to the rear surface of the fixed scroll outside the valve receiving groove. According to claim 1,
The retainer fixing part,
A compressor that extends from both sides of the valve fixing part in the circumferential direction and is fastened to the rear surface of the fixed scroll at both sides of the valve receiving groove. According to claim 2,
On the rear surface of the fixed scroll, retainer fixing grooves provided on both sides of the valve receiving groove in the circumferential direction and into which the retainer fixing part is inserted are formed,
The depth of the retainer fixing groove,
Compressor formed smaller than the depth of the valve receiving groove. According to claim 3,
A bolt fastening groove is formed in the retainer fixing groove to fasten a fastening bolt penetrating the retainer,
A plurality of bolt fastening grooves are formed in each of the retainer fixing grooves. According to claim 4,
The outer spacing between the bolt fastening grooves on both sides located at the edge of the bolt fastening grooves,
Compressor formed equal to the inner distance between the bolt fastening grooves on both sides located in the center. According to claim 4,
The outer spacing between the bolt fastening grooves on both sides located at the edge of the bolt fastening grooves,
A compressor formed larger than the inner gap between the bolt fastening grooves on both sides located in the center. According to claim 1,
At least one bolt fastening groove for fastening the retainer fixing part is formed on the rear surface of the fixed scroll,
At least one of the bolt fastening grooves,
A compressor overlapping the fixed wrap in the axial direction. According to claim 1,
One end of the valve accommodating groove is provided with the discharge port, and the other end of the valve accommodating groove is provided with a fixing pin so as to be coupled to the valve member. According to claim 8,
The valve member has a valve fixing hole through which the fixing pin passes,
A compressor having a pin fixing groove formed in the retainer to insert the fixing pin penetrating the valve member. According to claim 8,
The compressor is provided with a plurality of fixing pins at predetermined intervals in the radial direction. According to claim 1,
The retainer fixing part,
A compressor formed to be thinner than the valve fixing part and the valve support part. According to claim 1,
The retainer fixing part,
A compressor formed as a unitary body with the valve fixing part. According to claim 1,
The retainer fixing part,
A compressor assembled and coupled to the valve fixing part. According to claim 13,
A compressor having a coupling part formed between the retainer fixing part and the valve fixing part so that the retainer fixing part is fixed to the valve fixing part. According to claim 13,
The retainer fixing part,
A compressor formed of a different material from the valve fixing part. According to any one of claims 1 to 15,
The outlet is
a first discharge port communicating with the discharge pressure chamber of the compression chamber; and
It communicates with the intermediate pressure chamber of the compression chamber and includes a plurality of second discharge ports formed on both sides of the first discharge port,
The valve member,
a fixed end fixed to the fixed scroll; and
It includes an opening and closing end extending from the fixed end and having a first opening and closing portion for opening and closing the first outlet and a second opening and closing portion for opening and closing the second outlet,
The fixed end is
A compressor fixed between the fixed scroll and the retainer on an imaginary line passing through the center of the first discharge port in a radial direction. According to any one of claims 1 to 15,
The valve member,
a fixed end fixed to the fixed scroll; and
It extends from the fixed end and includes an opening and closing end for opening and closing the outlet,
The fixed end is
A compressor fixed between the fixed scroll and the retainer on an imaginary line passing through the center of the discharge port in a radial direction. A valve plate having at least one discharge port;
a valve member having one end formed with a fixed end fixed to the valve plate and the other end forming an opening/closing end for opening and closing the discharge port while attaching to and detaching from the valve plate; and
A retainer provided on the rear surface of the valve member, one end fixing the fixed end of the valve member to the valve plate, and the other end being spaced apart from the valve plate with the valve member interposed therebetween to limit the opening amount of the valve member Including,
A valve receiving groove is formed in the valve plate so that a portion of the valve member and the retainer are inserted,
The retainer,
a retainer fixing part fastened to the valve plate;
a valve fixing part extending from the retainer fixing part and being inserted into the valve receiving groove to fix the valve member; and
A valve support portion extending from the valve fixing portion, inserted into the valve receiving groove, and detachable from the valve member to limit the opening amount of the valve member,
The retainer fixing part,
A compressor fastened to the rear surface of the valve plate outside the valve receiving groove.

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