KR20240024604A - Scroll Compressor - Google Patents

Abstract

The present invention includes a housing having a discharge space; a rotating shaft installed inside the housing and rotating; a turning scroll installed on the rotation axis to enable turning; a fixed scroll coupled to the orbiting scroll, forming a compression chamber between the orbiting scroll and the orbiting scroll, and having a discharge port capable of discharging compressed refrigerant into the discharge space; and a discharge valve, one side of which is elastically guided and movable inside the housing, and the other side of which is spaced apart from the discharge port or inserted into the inner circumference of the discharge port to open and close the discharge port.

Description

Scroll Compressor

The present invention relates to a scroll compressor, and more specifically, to a scroll compressor that enables high efficiency under various operating conditions by reducing dead volume.

Generally, compressors are applied to vapor compression refrigeration cycles (hereinafter abbreviated as refrigeration cycles) such as refrigerators or air conditioners. Compressors can be classified into reciprocating, rotary, scroll, etc. depending on the method of compressing the refrigerant.

Among these, the scroll compressor is a compressor in which a compression chamber is formed between the fixed wrap of the fixed scroll and the orbiting wrap of the orbiting scroll by engaging the orbiting scroll with the fixed scroll fixed in the inner space of the sealed container and making a orbital movement.

In a scroll compressor, an orbiting scroll and a fixed scroll are interlocked and combined, and the orbiting scroll rotates relative to the fixed scroll to form a pair of compression chambers.

The compression chamber consists of a suction pressure chamber formed on the outside, an intermediate pressure chamber formed continuously with the volume gradually decreasing from the suction pressure chamber toward the center, and a discharge pressure chamber connected to the center of the intermediate pressure chamber. Generally, the suction pressure chamber is formed by penetrating the side of the fixed scroll, the intermediate pressure chamber is sealed, and the discharge pressure chamber is formed by penetrating the head plate portion of the fixed scroll.

Meanwhile, a heat pump refers to a device that absorbs heat from low-temperature heat and transfers it to high-temperature heat. The one that uses low-temperature heat is usually called a refrigerator, and the one that uses high-temperature heat is called a refrigerator. It is generally referred to as a heat pump.

There are various types of heat pumps, such as compression type, chemical type, absorption type, and adsorption type, depending on the method of absorbing and dissipating heat. In particular, in the compression type, a motor is used as the power source to drive the compressor, which is called an EHP (Electric Heat Pump). It is classified into a method and a GHP (Gas Heat Pump) method that uses a gas engine to drive the compressor.

The compressor applied to GHP is a mechanical (belt driven) type and has a very similar structure to the existing automobile air conditioning compressor.

In the development of a scroll compressor for GHP, optimization of the discharge system on the fixed scroll side is necessary for high efficiency under various operating conditions. In particular, the dead volume is determined by the head plate thickness of the fixed scroll (related to reliability) and reduces the volumetric efficiency of the compressor, which has a negative effect when designing for capacity reduction.

In addition, the reed valve is composed of three parts: a valve, a retainer, and a fastening bolt, and opening and closing is performed by the pressure difference between the compressed part of the compressor and the inside of the housing. Simply by covering the discharge port, the body volume is kept intact. Since the K value of the valve is determined by the type and shape of the material, the range of material selection is narrow, and the valve's responsiveness to various operating conditions is low.

In Patent Document 1, in a sealing structure in which the fastening surface of the first housing and the second housing fastened to each other by bolts is sealed with an O-ring on the inside of the bolt, the first housing and/or the second housing outside the O-ring 2 The fastening surface of the housing is formed to protrude in the circumferential direction and has a rib that can be buckled when fastened, and the fastening surface of the first housing and/or the second housing inner than the O-ring is short-circuited in the circumferential direction. A sealing structure of a housing is disclosed.

In addition, Patent Document 2 includes a housing, a motor provided in the housing, a rotating shaft rotated by the motor, a rotating scroll that rotates in conjunction with the rotating shaft, and a fixed device that forms a compression chamber together with the rotating scroll. It includes a scroll, and the housing includes: a center housing; a front housing that houses the motor; and a rear housing forming a discharge chamber that accommodates the refrigerant discharged from the compression chamber, and between the fixed scroll and the rear housing, an injection valve for opening and closing an injection passage that guides the refrigerant flowing in from the outside of the housing to the compression chamber. and an injection valve assembly including leak prevention means.

In the case of a scroll compressor in the prior art, since there are several holes related to discharge (modulation, bypass, discharge), a reed valve that is relatively easy to install is installed.

However, the head plate thickness of the fixed scroll is applied to the entire body, and when this head plate thickness is reduced, the stress at the root of the wrap is reduced, which has a negative effect on the reliability of the compressor.

In addition, since the K value of the valve is determined by the type and shape of the material, the range of material selection is narrow, and the responsiveness of the valve according to various operating conditions is low. Low responsiveness is caused by overcompression, which reduces the efficiency of the compressor.

Therefore, there is a need to develop a compressor structure that can be used with a lifting valve to increase the efficiency of the compressor, reduce material costs (or number of parts), and simplify the structure.

In addition, the development of a structure that can reduce the dead volume, enable high efficiency under various operating conditions, and reduce the speed or vibration of the impact is required.

WO2017-169523A1(2017.10.05) Public Patent Publication No. 10-2021-0118743 (2021.10.01)

The present invention was devised to solve the above problems, and the purpose of the present invention is to provide a scroll compressor to which a lifting valve can be applied to enable high efficiency of the compressor and reduction of material cost (or number of parts). It is provided.

More specifically, through the application of lifting valves. The aim is to provide a scroll compressor that can reduce the dead volume, enable high efficiency under various operating conditions, and reduce the speed or vibration of the impulse.

In order to solve the above problems, the scroll compressor of the present invention includes a housing having a discharge space; a rotating shaft installed inside the housing and rotating; a turning scroll installed on the rotating shaft to enable turning; a fixed scroll coupled to the orbiting scroll, forming a compression chamber between the orbiting scroll and the orbiting scroll, and having a discharge port capable of discharging compressed refrigerant into the discharge space; and a discharge valve on one side of which is elastically guided and movably disposed inside the housing, and on the other side, which is spaced apart from the discharge port or is inserted into the inner circumference of the discharge port to open and close the discharge port.

As a result, through a structure in which the discharge valve is guided inside the housing and spaced apart or inserted into the discharge port, it is possible to increase the efficiency of the compressor and reduce the material cost or number of parts.

The housing has a guide hole for guiding one side of the discharge valve on the inside facing the fixed scroll, and the discharge valve includes: a guide portion accommodated to be guided in the guide hole; And it may include an opening and closing part that is connected to the guide part and is spaced apart from the discharge opening or is inserted into the inner circumference of the discharge opening to open and close the discharge opening.

As the discharge valve is configured to include a guide part and an opening/closing part, the discharge valve is guided inside the housing and has a structure in which it is spaced apart or inserted into the discharge port, enabling high efficiency in various operating conditions by reducing the dead volume, and enabling high efficiency in various operating conditions. Vibration can be reduced.

The discharge valve may further include a movement limiter provided between the guide portion and the opening/closing portion, and restricting movement of the discharge valve in a state in which the opening/closing portion is inserted into the inner periphery of the discharge opening to close the discharge opening.

With the configuration of the movement limiter, the discharge port can be opened and closed while preventing the closing portion from flowing into the inside of the guide hole.

The discharge port may have a predetermined diameter so that the movement limiting portion passes at one end where the discharge valve is disposed, and may be provided with a jaw portion that limits movement of the movement limiting portion when the discharge port is closed.

Preferably, the diameter of the movement limiting portion may be smaller than the diameter of the jaw portion.

As the discharge port is provided with a ledge, a step may be provided within the fixed head plate portion, which allows the insertion depth of the discharge valve to become deeper, and the ledge forms a refrigerant flow path when the discharge port is open, The reduction of dead body volume within the discharge space can be maximized.

The housing has a guide hole that guides one side of the discharge valve on the inside facing the fixed scroll, and an elastic member receiving portion that is as large as a predetermined diameter is provided at one end of the guide hole, and the elastic member is provided at one end of the guide hole. An elastic member that elastically supports the discharge valve may be installed in the member receiving portion.

As a result, the discharge valve can be operated while being elastically supported by the elastic member.

Inside the housing, a bypass flow path may be further provided to intersect the guide hole to enable communication between the guide hole and the discharge space.

By providing a bypass passage inside the housing, the discharge valve allows compression and expansion generated inside the guide hole to be discharged to the outside of the guide hole when the discharge valve moves forward or backward.

The lower ends of the bypass passages may be in communication with each other so as to intersect at the lower ends of the guide holes.

The discharge valve may be inserted and installed inside the housing to be movable in an axial direction in which the rotation axis extends.

As a result, because the guide part is installed in the housing, unlike the existing configuration, a separate guide part and fastening-related members are unnecessary, and by increasing the mass of the guide part, the speed or vibration related to the impact amount (F = mv) is reduced. It works.

The discharge valve may be a lifting valve.

Due to this, the present invention enables reduction of dead volume without changing the design of the fixed scroll by a structure in which a simple lifting valve is installed in the guide hole, and the assembly process is improved through structural simplification.

The housing may be provided with a guide hole for guiding one side of the discharge valve on the inside facing the fixed scroll, and an elastic portion for elastically supporting the discharge valve may be installed at an outer end of the guide hole.

As a result, the discharge valve is elastically supported by the elastic portion, allowing the discharge valve to operate.

The elastic portion may be formed in a shape that is bent at least once.

The fixed scroll is spaced apart from the discharge port and is provided with at least one bypass hole for discharging part of the compressed refrigerant to prevent overcompression in the compression chamber. In the scroll compressor of the present invention, one side is located on the inside of the housing. It is arranged to be guided, and the other side may further include at least one bypass valve that is spaced apart from the bypass hole or inserted into the inner circumference of the bypass hole to open and close the bypass hole.

As a result, through a structure in which the bypass valve is guided inside the housing and spaced apart or inserted into the bypass hole, it is possible to increase the efficiency of the compressor and reduce the material cost or number of parts.

The housing has a guide hole for guiding one side of the bypass valve on the inside facing the fixed scroll, and the bypass valve includes: a guide portion accommodated to be guided in the guide hole; and an opening and closing part connected to the guide part and spaced apart from the bypass hole or inserted into the inner circumference of the bypass hole to open and close the bypass hole.

The bypass valve is provided between the guide part and the opening/closing part, and further includes a movement limiter that restricts movement of the bypass valve in a state where the opening/closing part is inserted into the inner circumference of the discharge port to close the bypass hole. can do.

The bypass hole has a predetermined diameter so that the movement limiter passes at one end where the bypass valve is disposed, and has a step portion that limits the movement of the movement limiter when the bypass hole is closed. can do.

As the bypass hole is provided with a step, a step may be provided within the fixed head plate portion, and as a result, the insertion depth of the bypass valve can be deepened, and the step may allow the refrigerant to flow when the bypass hole is open. By forming a flow path, the reduction of dead volume within the discharge space can be maximized.

The housing has a guide hole that guides one side of the bypass valve on the inside facing the fixed scroll, and an elastic member receiving portion that is as large as a predetermined diameter is provided at one end of the guide hole, An elastic member that elastically supports the bypass valve may be installed in the elastic member receiving portion.

Inside the housing, a bypass flow path may be further provided to intersect the guide hole to enable communication between the guide hole and the discharge space.

The lower ends of the bypass passages may be in communication with each other so as to intersect at the lower end of the guide hole.

In one example, the housing includes a middle housing to which the fixed scroll is coupled to an inner circumference; and a rear housing coupled to the middle housing and having at least one guide hole for accommodating at least one side of the discharge valve and the bypass valve to be guided.

The scroll compressor of the present invention has a structure in which the discharge valve is guided inside the housing and is spaced apart or inserted into the discharge port, enabling high efficiency of the compressor and reduction of material costs or number of parts.

In addition, the scroll compressor of the present invention has a structure in which the discharge valve is guided inside the housing and spaced apart or inserted into the discharge port, enabling high efficiency under various operating conditions by reducing the dead volume, and reducing the speed or vibration of the impact amount. do.

The scroll compressor of the present invention has a guide hole on the inside of the housing, the discharge valve is guided by the guide hole, and the discharge port is opened or closed, so that compared to the existing reed valve type valve, it has a simpler structure and allows the discharge of compressed refrigerant. Discharge and movement restrictions can be enabled.

1 is a schematic diagram showing a gas engine heat pump including a scroll compressor of the present invention.
Figure 2 is a cross-sectional view showing the scroll compressor of the present invention.
Figure 3 is an exploded perspective view showing a part of the scroll compressor of the present invention.
Figure 4a is a cross-sectional view showing an example in which the discharge valve is installed in the rear housing in the present invention.
Figure 4b is an exploded perspective view showing an example in which the discharge valve is installed in the rear housing in the present invention.
Figure 4c is a perspective view showing an example in which the discharge valve is installed in the rear housing in the present invention.
Figure 4d is a plan view showing an example in which the discharge valve is installed in the rear housing in the present invention.
Figure 5 is an exploded perspective view showing an example in which a discharge valve and a bypass valve are installed on a fixed scroll.
Fig. 6A is a cross-sectional view showing an example in which the discharge port of the fixed scroll is closed by the discharge valve.
Fig. 6B is a cross-sectional view showing an example in which the discharge port of the fixed scroll is opened by the discharge valve.
Fig. 7A is a cross-sectional view showing an example in which the discharge port of the fixed scroll is closed by the discharge valve and the discharge port is provided with a jaw.
Fig. 7B is a cross-sectional view showing an example in which the discharge port of the fixed scroll is opened by the discharge valve and the discharge port is provided with a jaw.
Figure 8a is an exploded perspective view showing another example of an elastic member installed in the discharge valve of the present invention.
Figure 8b is a cross-sectional view showing another example of an elastic member installed in the discharge valve of the present invention, but showing an example in which the discharge port of the fixed scroll is opened by the discharge valve.

Hereinafter, the scroll compressor 100 related to the present invention will be described in more detail with reference to the drawings.

In this specification, the same or similar reference numbers are assigned to the same or similar components even in different embodiments, and duplicate descriptions thereof are omitted.

In addition, even if the embodiments are different from each other, the structure applied to one embodiment may be equally applied to another embodiment as long as there is no structural or functional contradiction.

Singular expressions include plural expressions unless the context clearly dictates otherwise.

In describing the embodiments disclosed in this specification, if it is determined that detailed descriptions of related known technologies may obscure the gist of the embodiments disclosed in this specification, the detailed descriptions will be omitted.

The attached drawings are only for easy understanding of the embodiments disclosed in this specification, and the technical idea disclosed in this specification is not limited by the attached drawings, and all changes, equivalents, and changes included in the spirit and technical scope of the present invention are not limited. It should be understood to include water or substitutes.

FIG. 1 is a schematic diagram showing a gas engine heat pump 1000 including the scroll compressor 100 of the present invention, FIG. 2 is a cross-sectional view showing the scroll compressor 100 of the present invention, and FIG. 3 is a schematic diagram of the gas engine heat pump 1000 including the scroll compressor 100 of the present invention. This is an exploded perspective view showing a part of the scroll compressor 100.

Figure 1 is a schematic diagram showing a gas engine heat pump 1000 according to this embodiment.

Referring to FIG. 1, the gas engine heat pump 1000 according to this embodiment is configured such that the compressor 100, the condenser 194b, the expander 194c, and the evaporator 194d form a closed loop. That is, the condenser 194b, the expander 194c, and the evaporator 194d are sequentially connected to the discharge side of the compressor 100, and the evaporator 194d is connected to the suction side of the compressor 100.

In this embodiment, an oil separator 194e is provided on the discharge side of the compressor 100, that is, between the compressor 100 and the condenser 194b, and the first outlet side of the oil separator 194e is provided with a refrigerant connected to the condenser 194b. The circulation pipe 197 is connected to the second outlet side of the oil separator 194e and the oil return pipe 194e-2 is connected to the suction side of the compressor 100.

Hereinafter, with reference to FIGS. 1 to 3, the scroll compressor 100 of the present invention will be described.

The scroll compressor 100 of the present invention may be a horizontal scroll.

Additionally, the scroll compressor 100 of the present invention may be a GHP (Gas Heat Pump) type that uses a gas engine as a power source to drive the compressor.

The scroll compressor 100 of the present invention includes a housing 10, a rotating shaft 20, an orbiting scroll 30, a fixed scroll 40, and a discharge valve 61.

The housing 10 has a discharge space 10b.

The rotation shaft 20 is installed inside the housing 10 and rotates.

The orbiting scroll 30 is installed to be capable of orbiting and rotating on the rotation shaft 20.

The fixed scroll 40 is coupled to engage with the orbiting scroll 30 to form a compression chamber (V) between the orbiting scrolls 30, and an outlet ( 411).

The discharge valve 61 is arranged so that one side is guided inside the housing 10, and the other side is spaced apart from the discharge port 411 or inserted into the inner periphery of the discharge port 411 to open and close the discharge port 411. do.

The scroll compressor 100 of the prior art is equipped with a reed valve that is relatively easy to install because there are several holes related to discharge (modulation, bypass, discharge). However, the head plate thickness of the fixed scroll 40 is applied to the entire body, and when the head plate thickness is reduced, the stress at the root of the wrap is reduced, which has a negative effect on the reliability of the compressor.

The scroll compressor 100 of the present invention has a structure in which the discharge valve 61 is guided inside the housing 10 and is spaced apart or inserted into the discharge port 411, enabling high efficiency of the compressor and reducing material cost or number of parts. Reduction can be made possible.

In addition, the scroll compressor 100 of the present invention has a structure in which the discharge valve 61 is guided inside the housing 10 and is spaced apart or inserted into the discharge port 411, thereby reducing the dead volume and enabling high efficiency under various operating conditions. And it is possible to reduce the speed or vibration of the impulse.

First, referring to FIGS. 2 and 3, the orbiting scroll 30 will be described.

The orbiting scroll 30 is arranged to be capable of orbiting and rotating with respect to the fixed scroll 40 .

The orbiting scroll 30 is configured to form a compression chamber V together with the fixed scroll 40.

The orbiting scroll 30 is connected to a orbiting wrap 32 that engages the fixed wrap 42 of the fixed scroll 40 to form a compression chamber (V) at one end of the orbiting wrap 32 and has a predetermined width. It may be provided with a pivoting head plate portion 31 formed of and a shaft coupling portion 33 formed from the pivoting disk portion 31 in the opposite direction of the pivoting wrap 32.

The orbiting scroll 30 is disposed at a position facing the fixed scroll 40. The orbiting scroll 30 is coupled to the eccentric bush 25 of the rotating shaft 20. Accordingly, the orbiting scroll 30 is coupled to the rotation shaft 20 so as to be capable of orbiting.

The turning scroll 30, which receives rotational force through the eccentric bush 25, is prevented from rotating by the rotation prevention member 70 and makes a turning movement.

For example, the orbiting scroll 30 may be formed of aluminum or an alloy containing aluminum to be advantageous for high-speed orbiting rotational movement.

In the present invention, the orbiting scroll 30 shown in FIGS. 2 and 3 may be formed of the same material as the front housing 12, in which case, as shown in FIGS. 2 and 3, the orbiting scroll 30 may be formed of the same material as the front housing 12. A thrust plate 35 may be disposed between the scroll 30 and the front housing 12. However, the present invention is not necessarily limited to this structure.

As another example, the orbiting scroll 30 may be formed of a different material from the front housing 12. In this case, the orbiting scroll 30 and the front housing 12 can directly rub, and a separate thrust plate is not required between the orbiting scroll 30 and the front housing 12.

The orbiting scroll 30 may include a pivoting plate portion 31, a pivoting wrap 32, a shaft coupling portion 33, and a ring receiving groove 31a.

The rotating head plate portion 31 is formed in a plate shape corresponding to the fixed head plate portion 41 described later. If the pivoting disk portion 31 has a cross section corresponding to a circle, the pivoting disk portion 31 has the shape of a disk.

The rotating mirror plate portion 31 may be seated on the fixed wrap 42 of the fixed scroll 40. Additionally, the pivot plate portion 31 and the fixing wrap 42 may form a thrust surface.

When the side facing the front housing 12 of the two sides of the rotating mirror plate 31 is called the first side and the side facing the fixed scroll 40 is called the second side, the first side has a ring receiving groove 31a. is formed, and a turning wrap 32 is formed on the second side.

Figure 2 shows an example in which ring receiving grooves 31a are formed on the left and right sides (based on the cross section) of the first surface formed below the pivot plate portion.

The first surface may be understood as a surface connected to the front housing 12.

A plurality of ring receiving grooves 31a may be formed to be spaced apart from each other in the circumferential direction on the turning plate portion 31 of the turning scroll 30.

The anti-rotation ring 72 may be coupled to the ring receiving groove 31a by a press-fitting method. However, it is not necessarily limited to this coupling method by press fitting, and may be coupled by coupling methods other than screw coupling.

An anti-rotation pin 71, which will be described later, may be installed in the anti-rotation ring 72 coupled to the ring receiving groove 31a to enable rotation. The anti-rotation ring (72) is configured to rotate relative to the anti-rotation pin (71).

The ring receiving groove 31a may be formed in a circular shape with a closed periphery, or in some cases, may be formed in an arc shape with a portion of the periphery open. The ring receiving groove (31a) may be formed in a circular shape.

Due to the structure of the anti-rotation pin 71 and the anti-rotation ring 72, the orbiting scroll 30 can pivot while preventing rotation between the front housing 12 and the fixed scroll 40.

The turning wrap 32 is formed from an involute curve, an Archimedean spiral, or a logarithmic spiral from the second side of the turning plate 31 toward the fixed scroll 40. It protrudes into a shape. The orbiting wrap 32 may be formed in various other shapes.

The orbiting wrap 32 may be in close contact with the fixed head plate portion 41. Likewise, the fixing wrap 42 may also be in close contact with the pivot plate portion 31. A tip seal is installed in at least one of the axial end of the fixed wrap 42 and the axial end of the pivoting wrap 32 to seal the compression chamber (V).

A shaft coupling portion 33 is formed at the center of the pivot plate portion 31. The shaft coupling portion 33 protrudes from the first surface of the pivot plate portion 31 toward the fixed scroll 40. The shaft coupling portion 33 may be formed at a position corresponding to the base circle of the involute shape that defines the orbital wrap 32. Accordingly, the shaft coupling portion 33 forms the innermost part of the pivot wrap 32.

The pivot wrap 32 may extend to the outer peripheral surface of the pivot plate portion 31. Due to this, it is possible to maximize the suction volume by extending the wrap length of the orbiting wrap 32 to the maximum.

Additionally, the shaft coupling portion 33 may be formed in a cylindrical shape to accommodate the eccentric bush 25 installed on the rotating shaft 20. Alternatively, the shaft coupling portion 33 may be understood as a boss shape. The shaft coupling portion 33 is formed to surround the eccentric bush 25 installed on the rotating shaft 20.

A third bearing may be provided between the inner peripheral surface of the shaft coupling portion 33 and the outer peripheral surface of the eccentric bush 25. Referring to FIG. 2, the third bearing is shown as an example of a needle bearing, but is not necessarily limited thereto and may be a bushing bearing or a ball bearing.

The fixed scroll 40 and the orbiting scroll 30 are coupled to each other to form a pair of compression chambers (V). As the orbiting scroll 30 rotates, the volume of the compression chamber (V) changes repeatedly, and accordingly, fluid such as refrigerant is compressed in the compression chamber (V).

The fixed scroll 40 is disposed relatively far from the rotation axis 20, and the orbiting scroll 30 is disposed relatively close to the rotation axis 20. The fixed scroll 40 is disposed between the orbiting scroll 30 and the rear housing 13 in the axial direction. Additionally, the orbiting scroll 30 is disposed between the fixed scroll 40 and the front housing 12 in the axial direction.

FIG. 4A is a cross-sectional view showing an example in which the discharge valve 61 is installed in the rear housing 13 in the present invention, and FIG. 4B is a cross-sectional view showing an example in which the discharge valve 61 is installed in the rear housing 13 in the present invention. This is an exploded perspective view.

In addition, Figure 4c is a perspective view showing an example in which the discharge valve 61 is installed on the rear housing 13 in the present invention, and Figure 4d shows an example in which the discharge valve 61 is installed in the rear housing 13 in the present invention. This is a floor plan.

Hereinafter, the discharge valve 61 of the present invention will be described with reference to FIGS. 4A to 4D.

In the present invention, the discharge valve 61 is guided by the guide hole 13e of the housing 10, allowing the discharge port 411 to be opened or closed.

In the present invention, the housing 10 may be provided with a guide hole 13e. The guide hole 13e can guide one side of the discharge valve 61 on the inside facing the fixed scroll 40.

The guide hole 13e functions as a guide to stably advance and retreat the discharge valve 61.

The discharge valve 61 may be installed inside the housing 10 to be disposed in the discharge space inside the housing 10. Additionally, the discharge valve 61 may be installed to be movable relative to the housing 10. The discharge valve 61 is installed in the guide hole 13e of the housing 10 so as to be movable in the axial direction, and allows the discharge port 411 to be opened or closed.

Since the discharge valve 61 is installed in the housing 10, compared to the existing reed valve installed in the fixed scroll 40, a separate guide portion 61a or fastening-related member is not required. That is, the discharge valve 61 has a simple structure installed in the guide hole 13e inside the housing 10 so as to be relatively movable, thereby reducing the dead volume in the discharge space and ensuring high efficiency and reliability of the compressor. It becomes possible.

In the scroll compressor 100 of the present invention, the housing 10 may include a middle housing 11 and a rear housing 13. In addition, FIG. 2 and the like show an example in which the housing 10 further includes a front housing 12.

A fixed scroll 40 may be coupled to the inner periphery of the middle housing 11.

Additionally, the rear housing 13 may be coupled to one end of the middle housing 11. The guide hole 13e provided in the housing 10 may be provided, for example, inside the rear housing 13. The guide hole (13e) accommodates one side of the discharge valve (61) to guide it.

The guide hole 13e serves as a guide so that the discharge valve 61 can stably advance and retreat.

The guide hole 13e may be formed in the extending direction of the rotation axis, in the vertical direction in the drawing, as shown in FIGS. 3 and 4A.

The discharge valve 61 may be installed in the guide hole 13e of the rear housing 13.

Since the discharge valve 61 is installed in the guide hole 13e of the rear housing 13, there is no need for a separate guide portion 61a or fastening-related member compared to the existing reed valve. That is, the discharge valve 61 has a simple structure in which it is installed in the guide hole 13e on the inside of the rear housing 13 so as to be relatively movable, thereby reducing the dead body volume within the discharge space (first discharge space 10b1). This makes it possible to secure high efficiency and reliability of the compressor.

Figure 2 shows an example in which the front housing 12, middle housing 11, and rear housing 13 are each formed as separate members. However, it is not necessarily limited to this, and the housing 10 may be formed as a single member.

A fixed scroll 40 is coupled to the inner periphery of the middle housing 11. Additionally, the rear housing 13 is coupled to the middle housing 11 and has a guide hole 13e. The guide hole 13e is configured to accommodate one side of the discharge valve 61 so that one side of the discharge valve 61 is guided.

Meanwhile, in the present invention, the discharge valve 61 may be, for example, a lifting valve. In addition, the discharge valve 61 can be made of various materials from the viewpoint of operational efficiency and reliability.

Referring to FIG. 4A, the discharge valve 61 may include a guide portion 61a and an opening/closing portion 61b.

The guide portion 61a may be accommodated to be guided in the guide hole 13e. The guide portion 61a may be provided in a shape that matches the guide hole 13e. For example, it may be formed with a circular cross-section.

The opening and closing part 61b is connected to the guide part 61a and is spaced apart from the discharge port 411 or is inserted into the inner circumference of the discharge port 411 to enable opening and closing of the discharge port 411. The opening/closing portion 61b must be insertable into the inner circumference of the discharge port 411 so that the discharge port 411 can be closed. Therefore, the opening and closing portion 61b must be formed in a shape that matches the discharge port 411, and may have a circular cross-section, for example.

The opening/closing portion 61b may be provided with a sealing portion (not shown) to seal the portion in contact with the discharge port 411 to prevent leakage of refrigerant when the discharge port 411 is closed.

Meanwhile, referring to FIG. 6A, the vertical distance of the opening/closing part 61b is formed to be smaller than the vertical distance of the discharge port 411, so that it can be stably seated and closed on the upper surface of the fixed scroll 40. It must be done.

Referring to FIG. 4A, the discharge valve 61 may further include a movement limiter 61c.

The movement limiting part 61c is provided between the guide part 61a and the opening/closing part 61b, and the opening/closing part 61b is inserted into the inner circumference of the discharge port 411 to close the discharge port 411. ) is formed to limit the movement of.

The movement limiting part 61c may protrude in the lateral direction of the discharge valve 61 between the guide part 61a and the opening/closing part 61b. For example, the movement limiting part 61c may have a circular cross-section, and preferably has a larger diameter than the respective diameters of the guide part 61a and the opening/closing part 61b.

In addition, the movement limiter 61c must have a diameter larger than that of the discharge port 411 so that the movement of the discharge valve 61 is limited by the end of the discharge port 411.

Additionally, an elastic member receiving portion 13e-1 may be provided at one end of the guide hole 13e.

An elastic member 61d is installed in the elastic member receiving portion 13e-1, and the elastic member 61d elastically supports the discharge valve 61.

For this reason, the discharge valve 61 operates while being elastically supported between the guide hole 13e and the discharge port 411 of the fixed scroll 40, thereby enabling the discharge port 411 to be opened and closed.

The elastic member receiving portion 13e-1 may be provided with a jaw on which the elastic member 61d is seated.

The elastic member 61d may be, for example, a spring, and is formed to have a longer length than the elastic member receiving portion 13e-1, and rides between the discharge valve 61 and the jaw of the elastic member receiving portion 13e-1. Can behave sexually.

As described above, when the discharge valve 61 includes the movement limiting portion 61c, it may be disposed between the lower end of the movement limiting portion 61c and the jaw of the elastic member receiving portion 13e-1 ( Figure 4a).

Additionally, the housing 10 may be further provided with a bypass flow path 13e-2. The bypass passage 13e-2 may be provided inside the housing 10 to enable communication between the guide hole 13e and the discharge space, and is formed to intersect the guide hole 13e.

As described above, when the housing 10 is configured to include the middle housing 11 and the rear housing 13, the bypass passage 13e-2, like the guide hole 13e, is connected to the rear housing 13. ) can be provided on the inside.

The bypass flow path (13e-2) stores pressure for compression/expansion generated inside the guide hole (13e) when the discharge valve 61 advances and retreats within the guide hole (13e) into the discharge space (first discharge space). Allows detour to (10b1)).

As a result, reliability can be maintained by preventing problems such as abnormal behavior or malfunction of the discharge valve 61 due to the pressure caused by the refrigerant contained in the guide hole 13e being filled.

As shown in FIG. 2, the front housing 12, the middle housing 11, and the rear housing 13 may form the housing 10 that forms the exterior of the scroll compressor 100 of the present invention.

The fixed scroll 40 is supported by the middle housing 11 in the radial direction of the rotation axis 20. And the fixed scroll 40 is supported by the rear housing 13 in the axial direction of the rotation axis 20.

The orbiting scroll 30 is arranged to face the fixed scroll 40. The orbiting scroll 30 is coupled to the eccentric bush 25 of the rotating shaft 20. Accordingly, the orbiting scroll 30 is eccentrically coupled to the rotation shaft 20 and rotates eccentrically rather than concentrically. That is, the orbiting scroll 30 is coupled to the eccentric bush 25 and receives rotational force through the eccentric bush 25, and the orbiting scroll 30 is guided to prevent rotation by the rotation prevention member 70, Turning movement becomes possible.

In this way, the fixed scroll 40 is arranged to face the orbiting scroll 30. Since the orbiting scroll 30 is supported in the axial direction by the front housing 12, the fixed scroll 40 is also axially supported. It can be understood as a structure indirectly supported by the front housing 12.

The fixed scroll 40 includes a fixed head plate portion 41 and a fixed wrap 42.

The outer circumference of the fixed head plate portion 41 is fixedly coupled to the inner circumference of the middle housing 11, and the upper portion is supported by the rear housing 13 based on FIG. 2. Additionally, the fixed head plate portion 41 is formed in a plate shape. The fixed head plate portion 41 may have a circular cross section. In this case, the fixed head plate portion 41 has the shape of a disk.

If the side facing the rear housing 13 of the two sides of the fixed head plate 41 is called the first side, and the side facing the orbiting scroll 30 is called the second side, the first side has a partition protrusion 41c. And a bypass guide groove (41c-1) is formed, and a fixing wrap (42) is formed on the second surface.

The fixed wrap 42 protrudes toward the orbiting scroll 30 in the shape of an involute curve, an Archimedean spiral, or a logarithmic spiral. The fixed wrap 42 may be formed in various other shapes. The fixed wrap 42 engages with the orbiting wrap 32 to form a compression chamber (V).

A discharge port 411 is formed at the center of the fixed head plate portion 41. Referring to FIG. 2, in this embodiment, an example is shown in which one discharge port 411 is formed at the center of the fixed head plate portion 41.

The fixed scroll 40 may be provided with at least one bypass hole 412a. The bypass hole 412a is spaced apart from the discharge port 411 and can discharge a portion of the compressed refrigerant to prevent overcompression in the compression chamber (V).

For example, the bypass hole 412a may be formed to be spaced apart from the discharge port 411 in the fixed head plate portion 41.

FIG. 5 is an exploded perspective view showing an example in which the discharge valve 61 and the bypass valve 63 are installed on the fixed scroll 40, and FIG. 6A shows the discharge port 411 of the fixed scroll 40 by the discharge valve 61. ) is a cross-sectional view showing a closed example.

Additionally, FIG. 6B is a cross-sectional view showing an example in which the discharge port 411 of the fixed scroll 40 is opened by the discharge valve 61.

Hereinafter, referring to FIGS. 5 to 6B, the scroll compressor 100 of the present invention may further include at least one bypass valve 63.

The bypass valve 63 is arranged so that one side is guided inside the housing 10, and the other side is spaced apart from the bypass hole 412a or inserted into the inner periphery of the bypass hole 412a ( 412a) can be opened and closed.

Through a structure in which the bypass valve 63 is guided inside the housing 10 and spaced apart or inserted into the bypass hole 412a, it is possible to increase the efficiency of the compressor and reduce the material cost or number of parts. .

For example, the bypass valve 63, like the discharge valve 61, may be a lifting valve.

In addition, the bypass valve 63 can be made of various materials from the viewpoint of operational efficiency and reliability.

As described above, in the present invention, the housing 10 may be provided with a first guide hole 13e that guides one side of the discharge valve 61. Likewise, the housing 10 may further include a second guide hole 13f that guides one side of the bypass valve 63.

The second guide hole 13f guiding the bypass valve 63 may be named the bypass guide hole 13e to distinguish it from the guide hole 13e guiding the discharge valve 61.

Like the first guide hole 13e, the second guide hole 13f also serves as a guide so that the discharge valve 61 can stably advance and retreat.

The second guide hole 13f may be formed in the same structure as the first guide hole 13e. However, since the bypass hole 412a generally has a smaller diameter than the discharge hole 411, the second guide hole 13f may be formed with a smaller diameter than the first guide hole 13e.

An elastic member receiving portion 13f-1 may be provided at one end of the second guide hole 13f.

An elastic member 63d is installed in the elastic member receiving portion 13f-1, and the elastic member 63d elastically supports the bypass valve 63. For this reason, the bypass valve 63 is elastically supported and operated between the second guide hole 13f and the bypass hole 412a of the fixed scroll 40 to open and close the bypass hole 412a. .

The elastic member receiving portion 13f-1 may be provided with a jaw on which the elastic member 63d is seated.

The elastic member (step portion 412a-1) may be a spring, for example, and is formed to have a longer length than the elastic member accommodating portion 13f-1, thereby forming the bypass valve 63 and the elastic member accommodating portion 13f- 1) It can move elastically between the jaws.

As described above, when the bypass valve 63 includes the movement limiting portion 63c, it may be disposed between the lower end of the movement limiting portion 63c and the jaw of the elastic member receiving portion 13f-1. .

Additionally, the housing 10 may be further provided with a bypass flow path 13e-2. The bypass flow path 13e-2 may be provided inside the housing 10 to enable communication between the second guide hole 13f and the discharge space (first discharge space 10b1), and the guide hole 13e ) is placed in a direction that intersects.

As described above, when the housing 10 is configured to include the middle housing 11 and the rear housing 13, the bypass passage 13e-2, like the second guide hole 13f, is connected to the second guide hole 13f. It may be provided inside the rear housing 13 to intersect the guide hole 13f.

The bypass valve 63 may include a guide portion 63a and an opening/closing portion 63b.

The guide portion 63a may be accommodated to be guided in the guide hole 13e. The guide portion 63a may be provided in a shape that matches the guide hole 13e. For example, it may be formed with a circular cross-section.

The opening and closing part 63b is connected to the guide part 63a and is spaced apart from the bypass hole 412a or is inserted into the inner circumference of the bypass hole 412a to enable opening and closing of the bypass hole 412a. The opening/closing portion 63b must be insertable into the inner circumference of the bypass hole 412a so that the bypass hole 412a can be closed. Therefore, the opening and closing portion 63b must be formed in a shape that matches the bypass hole 412a, and may have a circular cross-section, for example.

As described above, the diameter of the bypass hole 412a may be smaller than the diameter of the bypass hole 412a. Therefore, the diameter of each of the opening and closing portion 63b of the bypass valve 63 and the guide portion 63a of the bypass valve 63 connected thereto is the diameter of the opening and closing portion 61b of the discharge valve 61 and the guide portion 63a connected thereto. It may be smaller than the diameter of the discharge valve 61. However, the shape of the bypass valve 63 may be the same as the shape of the discharge valve 61, although there is a difference in size.

The bypass valve 63 may further include a movement limiter (63c).

The movement limiting part 63c is provided between the guide part 63a and the opening/closing part 63b, and the opening/closing part 63b is inserted into the inner circumference of the bypass hole 412a to close the bypass hole 412a. It is formed to limit the movement of the bypass valve 63.

The movement limiting part 61c may protrude in the lateral direction of the discharge valve 61 between the guide part 61a and the opening/closing part 61b. For example, the movement limiting part 61c may have a circular cross-section, and preferably has a larger diameter than the respective diameters of the guide part 61a and the opening/closing part 61b.

One side of the discharge valve 61 can be guided on the inside facing the fixed scroll 40.

In the scroll compressor 100 of the present invention, the housing 10 may include a middle housing 11 and a rear housing 13. In addition, FIG. 2 and the like show an example in which the housing 10 further includes a front housing 12.

A fixed scroll 40 may be coupled to the inner periphery of the middle housing 11.

Additionally, the rear housing 13 may be coupled to one end of the middle housing 11. The guide hole 13e provided in the housing 10 may be provided, for example, inside the rear housing 13. The guide hole (13e) accommodates one side of the discharge valve (61) to guide it.

For example, the rear housing 13 has a rear flange portion at a side end, and the rear flange portion is coupled to the middle flange portion of the middle housing 11 with a bolt, so that the rear housing 13 is attached to the middle housing 11. can be combined

Meanwhile, the rear housing 13 may be made of cast iron. Since the rear housing 13 is made of cast iron, when the scroll compressor 100 of the present invention is applied to a commercial heat pump, the load is relatively large and the movement of the compressor is relatively high compared to when applied to an automobile air conditioning compressor. Since it is not necessary, it is advantageous in terms of reliability.

Referring to FIG. 5, an example is shown in the drawing in which bypass holes 412a are formed to be spaced apart in the upward and left directions of the discharge port 411, respectively, and each of the two bypass holes 412a is equipped with a bypass valve ( An example of 63) being installed is shown.

It is formed to be open and closed according to the pressure difference between the compression chamber (V) side and the opposite side, based on the bypass valve 63. For example, when the pressure in the compression chamber (V) increases, the bypass valve 63 is opened, and the refrigerant in the compression chamber (V) is discharged through the bypass hole (412a).

Hereinafter, the discharge port 411 and the bypass hole 412a formed in the fixed scroll 40 will be described.

At least one bypass hole 412a may be formed around the discharge port 411.

The bypass hole 412a is a passage through which refrigerant is discharged to prevent overcompression of the refrigerant.

The bypass hole 412a may be formed independently for each compression chamber (V) in the vicinity of the discharge port 411. For example, referring to FIGS. 2 and 3 , an example in which one bypass hole 412a is disposed on the left and right sides of the discharge port 411 is shown.

The discharge port 411 and the bypass hole 412a may each be opened and closed by a valve. For example, the discharge port 411 can be opened and closed by the discharge valve 61, and the bypass hole 412a can be opened and closed by the bypass valve 46.

Meanwhile, a capacity variable hole 412b, which is a hole through which the refrigerant is bypassed to change capacity, may be formed in the upper part of the fixed scroll 40.

Additionally, the capacity variable hole 412b may be formed independently for each compression chamber (V) at a position farther from the discharge port 411 than the bypass hole 412a.

The capacity variable hole 412b can be opened and closed by a valve. For example, the capacity variable hole 412b can be opened and closed by the capacity variable valve 47. For example, the capacity variable valve 47 may be a reed valve.

Meanwhile, a discharge space (10b) is formed between the rear surface of the fixed head plate portion (41) and the inner space of the rear housing (13) facing it, and the discharge space (10b) is divided into the first discharge space (10b1) and the second discharge space (10b1). It can be separated into a discharge space (10b2).

For example, a partition protrusion 41c extending toward the rear housing 13 by a preset height is formed on the rear surface of the fixed head plate 41 to form the first discharge space 10b1 and the second discharge space 10b2. can be made separable.

For example, as shown in FIGS. 2 and 3, a first discharge space 10b1 is formed outside the partition protrusion 41c, and a second discharge space 10b2 is formed inside the partition protrusion 41c. can be formed.

The first discharge space 10b1 may communicate with the refrigerant discharge port 13a described above, and the second discharge space 10b2 may communicate with the capacity variable port 13b described above. In other words, the second discharge space 10b2 may also be understood as a space for accommodating refrigerant by bypassing it so that capacity can be varied.

The discharge valve 61 and the bypass valve 46 belong to the first discharge space 10b1, and the capacity variable valve 47 belongs to the second discharge space 10b2.

Accordingly, the first discharge space 10b1 can discharge from the discharge pressure chambers of both compression chambers V (shown in the middle part of FIG. 2, communicating with the first discharge space) and guide it to the condenser 194b of the refrigeration cycle. Let's do it.

The second discharge space 10b2 stores the refrigerant bypassed from the intermediate pressure chamber of both compression chambers V (the second intermediate pressure chamber having a lower pressure than the first intermediate pressure chamber, shown on the side of the compression chamber V in FIG. 2). It flows into the return port (11b) through the capacity variable port (13b) and is recovered into the internal space of the casing, that is, the suction space.

The partition protrusion 41c may be formed only on the fixed head plate portion 41, but in some cases, it may also be formed on the front surface of the rear housing 13 facing the fixed head plate portion 41.

For example, as shown in FIG. 2, a first partition protrusion (for convenience, the reference numeral for the partition protrusion is used interchangeably) 41c is provided on the rear surface of the fixed head plate portion 41, and the front surface of the rear housing 13. The second compartment protrusions 13c may be formed to correspond to each other.

A bypass guide groove 41c-1 is formed inside the partition protrusion 41c. The bypass guide groove (41c-1) is formed in an approximately V-shape so as to accommodate the capacity variable holes (412b) of both compression chambers (V). When the compartment protrusion is divided into the first compartment protrusion (41c) and the second compartment protrusion (13c), the bypass guide groove (41c-1) is formed on the first compartment protrusion (41c) and the second compartment protrusion (13c), respectively. It may be, or it may be formed only on one compartment protrusion.

2 and 3A show an example in which the bypass guide groove 41c-1 is formed on the first section protrusion 41c.

The rotation shaft 20 is rotated by the generated power, and transmits this rotational force to the orbiting scroll 30 to enable the orbiting scroll 30 to orbit.

For example, the rotation shaft 20 is rotated by power transmitted through the clutch assembly 2 and can transmit the rotational force to the orbiting scroll 30.

The rotation axis may be rotatably installed on the inner periphery of the housing 10. For example, the rotation shaft 20 may be rotatably installed on the inner periphery of the front housing 12. In addition, the rotation shaft 20 is installed in the shaft coupling portion 33 of the orbiting scroll 30 to enable the orbiting scroll 30 to orbit and rotate.

Preferably, the rotation axis 20 may be arranged concentrically in the front housing 12.

The rotation shaft 20 may be supported by first and second bearings 85 and 86, which will be described later.

An eccentric bush 25 may be installed on the rotation shaft 20 to enable the orbiting scroll 30 to orbit and rotate. For this purpose, a coupling pin 22, to which the eccentric bush 25 is coupled, may be provided at the end of the rotating shaft 20 facing the orbiting scroll 30.

The eccentric bush 25 is provided with a coupling hole into which the coupling pin 22 is inserted so as to be eccentric with respect to the center of the eccentric bush 25.

The coupling pin 22 is provided at the rear end (upper part in FIG. 2) of the rotation axis 20 to be eccentric with respect to the center of the rotation axis 20. Additionally, an eccentric bush 25 is rotatably installed on the coupling pin 22.

Additionally, the eccentric bush 25 may be provided with a sub-balance weight 25a that assists the turning rotation of the turning scroll 30. The sub-balance weight 25a may be disposed on the outer periphery of the shaft coupling portion 33 of the orbiting scroll 30.

Figure 2 shows an example in which the sub-balance weight 25a is formed integrally with the eccentric bush 25, but it is not necessarily limited to this, and the sub-balance weight 25a is a separate member of the eccentric bush 25, such as bolting. It is also possible to combine by the method of .

In Figure 2, the orbiting scroll 30 has an eccentric bush 25 of the rotating shaft 20 coupled to the inside of the shaft coupling portion 33, and a sub-balance weight 25a is disposed on the outer periphery of the shaft coupling portion 33. An example is shown.

Accordingly, the rotation shaft 20 rotates due to the rotational force transmitted from the clutch assembly 2, and the eccentric bush 25 at the end of the rotation shaft 20 rotates eccentrically, so that the orbiting scroll 30 can pivot. .

Meanwhile, the rear housing 13 is formed in a substantially cylindrical shape with one end (front end, bottom in Figure 2) open and the other end (rear end, top in Figure 2) closed.

In the present invention, the front and rear can be understood as the front housing 12 side being the front and the rear housing 13 side being the rear, as can be seen from the names of the front housing 12 and rear housing 13. . However, in the present invention, for convenience in each drawing, the vertical direction may be described based on the drawings (that is, with respect to FIG. 2, the rear housing 13 is upper and the front housing 10 is lower).

In other words, the front end facing the fixed scroll 40 is open, while the rear end facing away from the fixed scroll 40 is closed.

Accordingly, the internal space of the rear housing 13 forms a discharge space 10b together with the rear surface of the fixed head plate 41, which will be described later, to accommodate the refrigerant discharged from the compression chamber V.

At the front end of the rear housing 13, a rear flange portion 13d bolted to the middle flange portion 11d described above extends in a flange shape. The second sealing member 82 described above is inserted between the rear flange portion 13d and the middle flange portion 11d and is bolted along the circumferential direction.

A third connection protrusion (not indicated) and a fourth connection protrusion (not indicated) are formed at the closed rear end of the rear housing 13. The third connection protrusion is formed at the center of the rear end of the rear housing 13, and the fourth connection protrusion is formed around the third connection protrusion. A refrigerant discharge port (13a) is formed on the third connection protrusion, and a capacity variable port (13b) is formed on the fourth connection protrusion. The refrigerant discharge port 13a and the capacity variable port 13b are formed by penetrating between the inner and outer surfaces of the rear housing 13, respectively.

Additionally, a refrigerant discharge port 13a may be provided on the side connected to the rear end of the rear housing 13. The refrigerant discharge port (13a) communicates with the first discharge space (10b1), allowing the refrigerant discharged from the compression chamber (V) to be guided to the condenser (194b) of the refrigeration cycle.

For example, the refrigerant discharge port 13a is connected to the refrigerant discharge pipe 116, allowing the discharged refrigerant to flow to the oil separator 194e, and after the oil is separated, the refrigerant circulation pipe 197 flows into the gas. It is provided as a condenser 194b forming the engine heat pump 1000 (FIG. 1).

The front housing 12 supports the orbiting scroll 30 so that it can rotate.

For example, the front housing 12 may support the second surface of the orbiting scroll 30 where the ring receiving groove 31a is formed.

The front housing 12 may be disposed between the clutch assembly 2 and the orbiting scroll 30.

The front housing 12 may be made of cast iron. Since the front housing 12 is formed of a cast iron material, when the scroll compressor 100 of the present invention is applied to a commercial heat pump, the load is relatively large and the movement of the compressor is difficult compared to when applied to an automobile air conditioning compressor. Since it is not necessary, it is advantageous in terms of reliability.

Meanwhile, the front housing 12 may be made of aluminum or cast iron to reduce the weight of the compressor when applied to a vehicle.

Meanwhile, the front housing 12 is coupled to the front end of the middle housing 11 and seals the suction space 10a, which is the inner space of the middle housing 11, while supporting the orbiting scroll 30 in the axial direction. . In this way, the front housing 12 forms a part of the housing 10 and also functions as a frame forming the compressed portion.

Hereinafter, the detailed configuration of the front housing 12 will be described.

The front housing 12 may include a housing flange portion 12a and a support wall portion 12b.

One side of the housing flange portion 12a faces the clutch assembly 2, and the other side faces the orbiting scroll 30.

In addition, the housing flange portion 12a is coupled to the middle flange portion 11d of the middle housing 11, so that the front housing 12 rotates the orbiting scroll 30 while being fixedly supported by the middle housing 11. It is supported so that it can rotate.

Additionally, as described above, the housing flange portion 12a may form part of the exterior of the compressor and function as a part of the housing 10.

Additionally, the housing flange portion 12a has a flange shape extending in the radial direction from the outer periphery of the front housing 12. For example, the housing flange portion 12a may have a circular cross-section. In this case, the housing flange portion 12a has the shape of a disk.

Additionally, the front housing 12 may be provided with shaft coupling portions 12d and 12f. A first shaft coupling portion 12d may be provided at the front end (lower side in FIG. 2) of the front housing 12. A rotation shaft 20 may be installed in the first shaft coupling portion 12d.

The shaft coupling portions 12d and 12f may include a first shaft coupling portion 12d with a small inner diameter on the front side and a second shaft coupling portion 12f with a large inner diameter on the rear side.

The first shaft coupling portion 12d may have a small inner diameter, and the second shaft coupling portion 12f may have a large inner diameter.

Referring again to FIG. 2, an example is shown in which the support wall portion 12b of the front housing 12 includes first and second shaft coupling portions 12d and 12f.

Additionally, first and second bearings 85 and 86 may be installed in the first and second shaft coupling portions 12d and 12f.

As shown in FIG. 2, the first and second bearings 85 and 86 may be ball bearings, but are not necessarily limited thereto and may be needle bearings or bushing bearings.

In addition, the orbiting scroll 30 is disposed adjacent to the second bearing 86, and as the vibration caused by the rotation of the orbiting scroll 30 is transmitted, the second bearing 86 has a higher load-bearing capacity than the first bearing 85. This can be done with large bearings.

As shown in FIG. 2, the lower portion (front) of the rotating shaft 20 is supported by the first bearing 85, and the upper portion of the rotating shaft 20 is supported by the second bearing 86.

Meanwhile, a mechanical seal 84 may be installed on the rotating shaft 20 between the first and second bearings 85 and 86 in the axial direction. The mechanical seal 84 may be installed between the rotating shaft 20 and the inner periphery of the front housing 12, and seals the front of the suction space 10a.

The mechanical seal 84 may include a fixed sealing body 84b and a rotating sealing body 84a.

The fixed seal (84b) is fixedly coupled to the inner peripheral surface of the shaft coupling portion (12d) provided in the front of the front housing (12), and the rotating seal (84a) is connected to the rotating shaft (20) in the lubrication space portion (12d-1). It can be coupled to the outer peripheral surface of the rotation shaft 20 to rotate together.

Accordingly, when the rotating shaft 20 rotates, the rotating sealing body 84a is in close contact with the fixed sealing body 84b, and the shaft receiving portion 12e and the lubricating space portion 12d-1 provided in the front of the front housing 12. ), that is, the front side of the suction space (10a) is sealed.

A support wall portion 12b may be formed on the surface of the housing flange portion 12a facing the orbiting scroll 30.

The support wall portion 12b may be formed to protrude on the surface of the housing flange portion 12a facing the orbiting scroll 30.

Additionally, the support wall portion 12b may be formed in a cylindrical structure with both ends open.

A rotation shaft 20 that transmits rotational force to the orbiting scroll 30 may be accommodated inside the support wall portion 12b.

In addition, a pivoting space 12b-1 is provided on the inner periphery of the support wall portion 12b. The pivoting space 12b-1 is a space in which the coupling portion 33 of the pivoting scroll 30 pivots and serves as a bearing space. It may be formed to communicate with the internal space of the unit, etc.

The diameter of the outer circumference of the support wall portion 12b must be formed to be larger than the diameter of the pivot plate portion 31. In addition, the support wall portion 12b preferably has a predetermined width so as to maintain sufficient rigidity to support the orbiting scroll 30 so that it can rotate.

The support wall portion 12b may be disposed inside a predetermined distance in the radial direction from the outer periphery of the housing flange portion 12a.

Additionally, the outer peripheral surface of the support wall portion 12b is in close contact with the inner peripheral surface of the middle housing 11. Accordingly, the housing flange portion 12a can be fixed to the inside of the middle housing 11.

The support wall portion 12b is provided with a turning support surface 12a-1 that supports the turning scroll 30 so that it can turn and rotate. 2 and 4, a pivoting support surface 12a-1 is provided on the upper surface of the support wall portion 12b, and a thrust plate 35 is provided between the pivoting support surface 12a-1 and the pivoting scroll 30. Can be installed.

That is, the thrust plate 35 is installed between the front housing 12 and the orbiting scroll 30.

It can be understood as being formed on the “rear surface” of the support wall portion 12b.

Meanwhile, an anti-rotation pin 71 and an oil supply groove 12c, which will be described later, may be formed on the pivoting support surface 12a-1.

Meanwhile, as shown in FIG. 2, the support wall portion 12b may be inserted into the inner periphery of the middle housing 11. Additionally, the front housing 12 may be coupled to the middle housing 11 by shrink fitting or welding.

Additionally, the support wall portion 12b may be formed integrally with the housing flange portion 12a. However, it is not necessarily limited to this, and the support wall portion 12b may be formed as a separate member from the housing flange portion 12a and may be coupled to each other with bolts or the like. In this case, the components such as the above-described first and second bearings 85 and 86 and the mechanical seal 84 can be easily assembled.

The rotation prevention member 70 is formed to cause the orbiting scroll 30 to rotate while preventing the orbiting scroll 30 from rotating. Without the rotation prevention member 70, the orbiting scroll 30 would rotate by the driving force transmitted by the rotation shaft 20. That is, the rotation of the orbiting scroll 30 is prevented by the rotation prevention member 70 and the orbiting scroll 30 is allowed to rotate.

The anti-rotation member 70 may include an anti-rotation pin 71 and an anti-rotation ring 72. The anti-rotation pin 71 and the anti-rotation ring 72 may each be provided in plural numbers. Referring to FIG. 3, although not clearly shown, six anti-rotation pins 71 and six anti-rotation rings 72 may be provided. However, it is not limited to this, and the anti-rotation pins 71 and anti-rotation rings 72 may be provided in different numbers.

Hereinafter, the structures of the anti-rotation pin 71 and the anti-rotation ring 72 will be described.

The turning support surface 12a-1 is provided with an anti-rotation pin 71 that protrudes toward the turning scroll 30.

The anti-rotation pin 71 may be provided as a separate member. In this case, a pin coupling hole 12a-2 into which the anti-rotation pin 71 is coupled may be formed in the pivoting support surface 12a-1. A plurality of pin coupling holes (12a-2) are formed to couple the anti-rotation pins (71), and the plurality of pin coupling holes (12a-2) may be arranged to be spaced apart from each other along the circumferential direction.

However, the anti-rotation pin 71 is not necessarily limited to a structure in which it is installed as a separate member, and the anti-rotation pin 71 may be formed integrally with the pivoting support surface 12a-1.

An oil supply groove 12c, which will be described later, may be provided between the pivoting support surface 12a-1 and the anti-rotation pin 71.

Meanwhile, in the anti-rotation ring 72 coupled to the ring receiving groove 31a of the above-described orbiting scroll 30, an anti-rotation pin 71 provided on the orbiting support surface 12a-1 is installed to enable rotation. It can be. The anti-rotation ring (72) is configured to rotate relative to the anti-rotation pin (71).

The anti-rotation ring 72 is restricted in its radial movement by the anti-rotation pin 71, preventing rotation and making a turning movement like the turning scroll 30.

The anti-rotation ring 72 is fixedly or rotatably inserted into the ring receiving groove 31a. In addition, an anti-rotation pin 71 is slidably inserted into the anti-rotation ring 72 along the circumferential direction on the inner circumference of the anti-rotation ring 72. The anti-rotation ring 72 may have the shape of a circular ring or a C-shape with one side open. In the present invention, an example formed in the shape of a circular ring, similar to the ring receiving groove (31a), is shown.

Due to the structure of the anti-rotation pin 71 and the anti-rotation ring 72, the orbiting scroll 30 can pivot and rotate between the front housing 12 and the fixed scroll 40.

Meanwhile, an oil supply groove 12c that allows oil to be supplied to the surface between the front housing 12 and the orbiting scroll 30 may be formed in the support wall portion 12b.

The oil supply groove 12c may be formed concavely in the pivoting support surface 12a-1 of the support wall portion 12b.

The oil supply groove 12c may be formed in at least one of a circumferential direction and a radial direction intersecting the pivoting support surface 12a-1.

For this reason, the oil contained in the inner periphery of the housing 10 flows from the turning support surface 12a-1 through the oil supply groove 12c of the front housing 12 as the turning scroll 30 rotates. It can flow, and oil can be supplied between the front housing 12 and the orbiting scroll 30, thereby improving reliability.

A suction space 10a is provided inside the housing 10, and the reservoir space 10c is located in the lower half of the suction space 10a (in the case of a horizontal scroll where the right side is in the lower half position and the left side is in the upper half position based on FIG. 2, It forms the right portion inside the housing 10). Oil is stored in the oil storage space 10c, and oil can be supplied between the front housing 12 and the orbiting scroll 30 through the oil supply groove 12c.

Meanwhile, the oil may be oil supplied from an oil recovery device that separates oil from the refrigerant discharged from the compression chamber (V) and returns it to the compressor.

For example, a plurality of oil supply grooves 12c may be formed, and the plurality of oil supply grooves 12c may be spaced apart from each other in the circumferential direction, and the front housing 12 may be formed on the pivoting support surface 12a-1. ) can be formed by penetrating the inner and outer circumference of the.

The scroll compressor 100 of the present invention may further include a clutch assembly (2).

The clutch assembly 2 may include a clutch plate 2a, a pulley 2b, and a coil portion 2c.

When power is applied to the externally provided electric unit (not shown) and the electric motor is driven, the clutch plate 2a connected thereto is driven, and the clutch plate 2a, including the pulley 2b and the coil part 2c, is driven. Enables operation of the clutch assembly (2).

The pulley 2b can be rotated by receiving power generated from an externally provided electric drive unit.

A belt, etc. may be installed on the pulley 2b so that externally generated power can be transmitted. The rotation shaft 20 is rotated by the rotation of the pulley 2b, allowing the orbiting scroll 30 to orbit and rotate.

For example, the pulley 2b of the clutch assembly 2 may rotate by transmitting power generated from an externally provided electric drive unit to the pulley 2b coupled to the external electric drive unit. In this case, the pulley coupled to the external transmission unit is a drive pulley that rotates directly by the external transmission unit, and the pulley 2b of the clutch assembly 2 is connected to the drive pulley 2b by a belt and rotates indirectly. It can be understood as a homogeneous pulley (2b).

FIG. 7A is a cross-sectional view showing an example in which the discharge port 411 of the fixed scroll 40 is closed by the discharge valve 61 and the discharge port 411 is provided with a jaw portion 411a, and FIG. 7B is a view showing an example of the discharge valve 61 ) This is a cross-sectional view showing an example in which the discharge port 411 of the fixed scroll 40 is opened and the discharge port 411 is provided with a jaw portion 411a.

Hereinafter, with reference to FIGS. 7A and 7B, an example in which the outlet 411 of the fixed scroll 40 is provided with a ridge 411a and the bypass hole 412a is provided with a step 412a-1. Describe about it.

Referring to FIGS. 7A and 7B, the discharge port 411 has a predetermined diameter so that the movement limiter 61c passes at one end where the discharge valve 61 is disposed, and the discharge port 411 ) may be provided with a jaw portion 411a that limits the movement of the movement limiting portion 61c in a closed state.

Preferably, the diameter of the movement limiting portion 61c of the discharge valve 61 may be smaller than the diameter of the jaw portion 411a. The diameter of the jaw portion 411a may be the diameter of the side of the jaw portion 411a.

As the discharge port 411 is provided with the jaw portion 411a, a step may be provided within the fixed head plate portion 41, and as a result, as shown in FIG. 7A, the insertion depth of the discharge valve 61 is further increased. It can be deeper, and as shown in FIG. 7b, when the discharge port 411 is open, the jaw portion 411a forms a refrigerant flow path, thereby reducing the dead volume within the discharge space (first discharge space 10b1). can be further maximized.

Meanwhile, as shown in FIGS. 7A and 7B, the bypass hole 412a has a predetermined diameter so that the movement limiter passes at one end where the bypass valve 63 is disposed, and A stepped portion 412a-1 may be provided to limit the movement of the movement limiting portion when the bypass hole 412a is closed.

As the bypass hole 412a is provided with a step portion 412a-1, a step may be provided within the fixed head plate portion 41, and as a result, the insertion depth of the bypass valve 63 becomes deeper. In a state in which the bypass hole 412a is open, the step portion 412a-1 forms a refrigerant flow path, so that the reduction in dead volume within the discharge space (first discharge space 10b1) can be maximized. .

In addition, referring to FIGS. 7A and 7B, the diameter of the side of the jaw portion 411a through which the movement limiting portion 61c of the discharge valve 61 passes is slightly larger than the diameter of the movement limiting portion 61c of the discharge valve 61. It must be structured so as to accommodate the movement limiting portion 61c of the discharge valve 61. Likewise, the diameter of the side of the step portion 412a-1 through which the movement limiting portion 63c of the bypass valve 63 passes is formed to be slightly larger than the diameter of the bypass valve 63, thereby preventing the movement of the bypass valve 63. It must have a structure that can accommodate the restriction portion 63c.

7A and 7B, except that the discharge port 61 is provided with a ridge 411a and the bypass hole 412a is provided with a step 412a-1. 7A and 7B, except that the discharge port is provided with a ridge portion 411a and the bypass hole 412a is provided with a stepped portion 412a-1. This will be replaced with the explanation of Figures 6a and 6b.

Figure 8a is an exploded perspective view showing another example of an elastic member 61d installed in the discharge valve 61 of the present invention, and Figure 8b is an exploded perspective view showing another example of an elastic member 61d installed in the discharge valve 61 of the present invention. This is a cross-sectional view showing an example where the discharge port 411 of the fixed scroll 40 is opened by the discharge valve 61.

Hereinafter, with reference to FIGS. 8A and 8B, an example in which another elastic portion 61e is provided in each of the discharge valve 61 and the bypass valve 63 will be described.

The structures of the discharge valve 61 and the bypass valve 63 shown in FIGS. 8A and 8B are the same as those of FIGS. 4A to 6B except that the elastic portion 61e in the form of a leaf spring is applied. , Replaced with the previous explanation.

The housing 10 has a guide hole 13e for guiding one side of the discharge valve 61 on the inside facing the fixed scroll 40, and a discharge valve 61 at the outer end of the guide hole 13e. An elastic portion 61e that elastically supports may be installed.

Since the elastic portion 61e is disposed at the outer end of the guide hole 13e, the rear housing 13 is not formed to accommodate the elastic portion 61e.

The elastic part 61e may be formed in a shape that is bent at least once. An example of the elastic part 61e in a shape that is bent twice is shown in FIGS. 8A and 8B.

The elastic portion 61e may be a leaf spring of the shape shown, or may also be formed in the form of a ring spring.

As a result, the discharge valve 61 can be operated while being elastically supported by the elastic portion 61e. In addition, by the elastic portion 61e, the discharge valve 61 can be elastically supported without the need for an elastic member receiving portion 13e-1 in the housing 10 or the rear housing 13. It becomes possible.

Hereinafter, the operation of the scroll compressor 100 according to the present invention will be described.

That is, when operation of the gas engine heat pump 1000 configured such that the scroll compressor 100, the condenser 194b, the expander, and the evaporator form a closed loop is selected, the clutch assembly 2 transmits the driving force to the rotating shaft 20. I do it. The driving force transmitted to the rotating shaft 20 is transmitted to the orbiting scroll 30 through the rotating shaft 20.

Then, while the orbiting scroll 30 is supported on the front housing 12, it rotates as much as the eccentric distance of the eccentric bush 25, and at the same time, the suction chamber is formed between the orbiting wrap 32 and the fixed wrap 42. , two pairs of compression chambers (V) consisting of an intermediate pressure chamber and a discharge chamber are formed in succession. The volume of the compression chamber (V) decreases as it moves toward the center by the continuous turning movement of the orbiting scroll (30), and the refrigerant is compressed while moving along the compression chamber (V) and passes through the discharge port (411) into the discharge space (10b). ), that is, it is discharged into the first discharge space 10b1 of FIG. 2.

At this time, the discharge valve 61 moves upward in FIG. 6b due to the pressure of the high-pressure refrigerant in the compression chamber (V), and as the opening/closing part 61b is spaced away from the discharge port 411, the discharge port 411 is opened. Thus, the high-pressure refrigerant is supplied to the oil separator 194e through the refrigerant discharge port 13a through the discharge space.

In addition, due to the pressure of the high-pressure refrigerant in the compression chamber (V), the bypass valve 63, like the discharge valve 61, moves upward in FIG. 6B, opening the bypass hole 412a, High-pressure refrigerant is supplied to the oil separator (194e) through the refrigerant discharge port (13a) through the discharge space.

Meanwhile, the capacity variable hole 412b is opened and closed by the capacity variable valve 47, so that some of the refrigerant in the compression chamber V flows into the second discharge space 10b2. Afterwards, it flows into the return port (11b) through the refrigerant recovery pipe (198a).

After refrigerant compression is performed, when the pressure in the compression chamber (V) is lowered, the discharge valve 61 moves downward by the elastic force of the elastic member 61d in Figure 6a, and the opening and closing portion 61b It is inserted into the inner circumference of the discharge port 411 to close the discharge port 411, thereby blocking the flow of refrigerant into the discharge space.

In addition, due to the pressure of the high-pressure refrigerant in the compression chamber (V), the bypass valve 63, like the discharge valve 61, moves downward due to the elastic force of the elastic member 61d in FIG. 6A. By closing the pass hole 412a, the flow of refrigerant into the discharge space is blocked.

The present invention enables high efficiency of the compressor and reduction of material cost or number of parts through a structure in which the discharge valve 61 is guided inside the housing 10 and is spaced apart or inserted into the discharge port 411. there is.

In addition, as the discharge valve 61 is configured to include a guide portion 61a and an opening/closing portion 61b, the discharge valve 61 is guided inside the housing 10 and is spaced apart from or inserted into the discharge port 411. Through this, the dead volume can be reduced, enabling high efficiency under various operating conditions, and reducing the speed or vibration of the impact amount.

The scroll compressor 100 described above is not limited to the configuration and method of the embodiments described above, and the embodiments may be configured by selectively combining all or part of each embodiment so that various modifications can be made.

It is obvious to those skilled in the art that the present invention can be embodied in other specific forms without departing from the spirit and essential features of the present invention. Accordingly, the above detailed description should not be construed as restrictive in all respects and should be considered illustrative. The scope of the present invention should be determined by reasonable interpretation of the appended claims, and all changes within the equivalent scope of the present invention are included in the scope of the present invention.

1000: Gas engine heat pump
100: Scroll compressor
10: Housing 10b: Discharge space
10b1: first discharge space 10b2: second discharge space
13a: Refrigerant discharge port 13e, 13f: Guide hole
13e-1, 13f-1: Elastic member receiving portion 13e-2: Bypass flow path
194b: Condenser 197: Refrigerant circulation pipe
194e: Oil separator 194e-2: Oil return pipe
194c: expander 194d: evaporator
198a: Refrigerant recovery pipe
198a: First control valve
115: Refrigerant suction pipe 116: Refrigerant discharge pipe
30: Orbiting scroll
40: Fixed scroll 411: Discharge port
412a: Bypass hole 412b: Capacity variable hole
61: Discharge valve 61a: Guide part
61b: opening and closing part 61c: movement restriction part
61d: elastic member 61e: elastic part
63: Bypass valve

Claims (20)

A housing having a discharge space;
a rotating shaft installed inside the housing and rotating;
a turning scroll installed on the rotation axis to enable turning;
a fixed scroll coupled to the orbiting scroll, forming a compression chamber between the orbiting scroll and the orbiting scroll, and having a discharge port capable of discharging compressed refrigerant into the discharge space; and
One side is elastically guided and movable inside the housing, and the other side is spaced apart from the discharge port or is inserted into the inner circumference of the discharge port and includes a discharge valve that opens and closes the discharge port.
According to paragraph 1,
The housing has a guide hole for guiding one side of the discharge valve on the inside facing the fixed scroll,
The discharge valve is,
a guide portion accommodated to be guided in the guide hole; and
A scroll compressor including an opening and closing portion connected to the guide portion and spaced apart from the discharge port or inserted into an inner circumference of the discharge port to open and close the discharge port.
According to paragraph 2,
The discharge valve is,
A scroll compressor provided between the guide part and the opening/closing part, further comprising a movement limiter that restricts movement of the discharge valve in a state where the opening/closing part is inserted into the inner periphery of the discharge opening to close the discharge opening.
According to paragraph 3,
The discharge port is,
A scroll compressor having a predetermined diameter so that the movement limiter passes at one end where the discharge valve is disposed, and a jaw portion that restricts movement of the movement limiter when the discharge port is closed.
According to paragraph 4,
A scroll compressor in which the diameter of the movement limiting portion is smaller than the diameter of the jaw portion.
According to paragraph 1,
The housing has a guide hole for guiding one side of the discharge valve on the inside facing the fixed scroll,
A scroll compressor in which an elastic member accommodating part is provided at one end of the guide hole to be as large as a predetermined diameter, and an elastic member for elastically supporting the discharge valve is installed in the elastic member accommodating part.
According to clause 6,
A scroll compressor further provided inside the housing to intersect the guide hole to enable communication between the guide hole and the discharge space.
In clause 7,
A scroll compressor in which the lower ends of the bypass passages communicate with each other so as to intersect at the lower ends of the guide holes.
According to paragraph 1,
The discharge valve is inserted and installed inside the housing to be movable in an axial direction in which the rotation shaft extends.
According to paragraph 1,
The discharge valve is a scroll compressor that is a lifting valve.
According to paragraph 1,
The housing has a guide hole for guiding one side of the discharge valve on the inside facing the fixed scroll,
A scroll compressor in which an elastic part for elastically supporting the discharge valve is installed at an outer end of the guide hole.
According to clause 11,
The elastic portion is a scroll compressor formed in a shape that is bent at least once.
According to paragraph 1,
The fixed scroll is provided with at least one bypass hole that is spaced apart from the discharge port and discharges a portion of the compressed refrigerant to prevent overcompression in the compression chamber,
One side is arranged to be guided inside the housing, and the other side is spaced apart from the bypass hole or inserted into the inner circumference of the bypass hole, and further includes at least one bypass valve to open and close the bypass hole.
According to clause 13,
The housing has a guide hole for guiding one side of the bypass valve on the inside facing the fixed scroll,
The bypass valve is,
a guide portion accommodated to be guided in the guide hole; and
A scroll compressor including an opening and closing portion connected to the guide portion and spaced apart from the bypass hole or inserted into an inner circumference of the bypass hole to open and close the bypass hole.
According to clause 14,
The bypass valve is,
A scroll compressor provided between the guide part and the opening and closing part, further comprising a movement limiter that restricts movement of the bypass valve in a state where the opening and closing part is inserted into the inner circumference of the bypass hole to close the bypass hole.
According to clause 15,
The bypass hole is,
A scroll compressor having a predetermined diameter so that the movement limiting part passes at one end where the bypass valve is disposed, and having a step for restricting movement of the movement limiting part when the bypass hole is closed.
According to clause 13,
The housing has a guide hole for guiding one side of the bypass valve on the inside facing the fixed scroll,
A scroll compressor in which an elastic member receiving portion is provided at one end of the guide hole to be as large as a predetermined diameter, and an elastic member for elastically supporting the bypass valve is installed in the elastic member receiving portion.
According to clause 17,
A scroll compressor further provided inside the housing to intersect the guide hole to enable communication between the guide hole and the discharge space.
According to clause 18,
A scroll compressor in which the lower ends of the bypass passages communicate with each other so as to intersect at the lower ends of the guide holes.
According to any one of claims 1 to 19,
The housing is,
a middle housing to which the fixed scroll is coupled to the inner circumference; and
A scroll compressor including a rear housing coupled to the middle housing and having at least one guide hole for accommodating one side of at least one of the discharge valve and the bypass valve.