JP2501182B2 - Refrigeration equipment - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration system using a scroll compressor for refrigeration and air conditioning.

[0002]

2. Description of the Related Art A conventional refrigeration system using a scroll compressor, as disclosed in Japanese Utility Model Laid-Open No. 56-85087, scroll-compresses a part of the refrigerant liquefied by a condenser of the refrigeration system. There is a refrigerating device provided with a pipe for injecting a liquid refrigerant to be introduced into a compression chamber of a machine.

[0003]

In scroll compressors, the pressure inside the compression chamber normally exhibits a pulsating pressure of several kg / cm ² . In the operating conditions of the refrigeration system, the operating pressure ratio may be low. As shown in FIG. 16, the scroll compressor has a scroll wrap winding number of around 2.5 to 3 turns. Since the scroll compressor has a constant displacement compressor structure, the maximum pressure Pmax is obtained in the innermost chamber inside the compression chamber. In the refrigerating apparatus of the above cited example, it is usual to compare the value of the maximum pressure Pmax, which is the internal pressure of the scroll compressor, with the pressure of the condenser on the refrigerating apparatus side, that is, the discharge pressure Pd. In particular, under a low pressure ratio condition, it becomes an overcompression operation condition and the discharge pressure Pd and the maximum pressure Pm of the innermost chamber are reached.
The relationship with ax is Pd <Pmax. In this case,
The refrigerant gas and the liquid refrigerant in the compression chamber have a (Pmax-Pd) differential pressure toward the upstream side of the liquid refrigerant injection pipe side of the refrigerating device through the liquid refrigerant injection pores provided in the scroll end plate portion. It will flow backwards. Therefore, several kg / in the innermost chamber
With the pulsating pressure of cm ^2, the backflow action of the refrigerant gas and the liquid refrigerant also exhibits a pulsating flow. Therefore, there is a problem that a hunting phenomenon or a malfunction of the auxiliary expansion valve occurs in the valve operation of the auxiliary expansion valve. In addition, the life of the auxiliary expansion valve will be adversely affected. Further, if there is the above-mentioned backflow phenomenon, gas refrigerant is mixed into the main refrigerant pipe side, which causes a problem that the performance of the evaporator of the refrigerating apparatus is deteriorated.

[0004]

In order to solve the above problems and problems, the present invention is for injecting a liquid refrigerant for introducing a part of a refrigerant liquefied in a condenser of a refrigeration system into a compression chamber of a scroll compressor. A refrigeration apparatus having a pipe is provided with a check valve in the liquid refrigerant injection pipe. Alternatively, the liquid refrigerant injection pipe is provided with a sub-expansion valve, and the check valve is arranged downstream of the sub-expansion valve. Further, in the scroll compressor, it is characterized in that a fine hole is provided in substantially the central portion between the wraps of the tooth bottom of the fixed scroll wrap, and the fine hole and the liquid refrigerant injection pipe are connected. Is.

[0005]

The operation of the present invention will be described with reference to FIG.
15, in the refrigeration apparatus including the liquid refrigerant injection pipe 62, the check valve 68 is arranged on the downstream side of the liquid refrigerant injection pipe 62 even under a low pressure ratio condition. When the refrigerant gas and the liquid refrigerant in the compression chamber are operated, the sub-expansion valve 67 on the liquid refrigerant injection pipe 62 side passes through the liquid refrigerant injection pores 63 provided in the scroll end plate portion 5a.
It will not flow backwards. In addition, several kg of innermost chamber /
The pulsating flow of the liquid medium gas and the liquid refrigerant due to the pulsating pressure of cm ² does not affect the auxiliary expansion valve 67. Even one pair of compression chambers is a single liquid refrigerant injection pipe, so compared to the conventional two liquid refrigerant injection pipes, the internal volume of the liquid refrigerant injection pores and the check valve is called dead volume Is reduced to about half, the internal leakage between the scroll compression chambers is reduced, and the compression power is reduced to improve the performance of the compressor, which is an effect peculiar to the scroll compressor. Further, since the flow of the liquid refrigerant in the liquid refrigerant injection pipe 62 becomes a unidirectional flow, vibration of the liquid refrigerant injection pipe 62 is reduced, and noise such as fluid noise can be reduced. Then, the sub expansion valve 6
The valve operation of 7 is stabilized, and the malfunction of the auxiliary expansion valve can be eliminated. In addition, the life of the auxiliary expansion valve can be extended. Further, by eliminating the backflow phenomenon, the high temperature gas refrigerant in the middle of compression, it is possible to avoid the phenomenon of mixing into the main refrigerant pipe side through the liquid refrigerant injection pipe, the pressure loss of the liquid refrigerant main pipe and the refrigeration device It has the effect of preventing the deterioration of the overall performance.

[0006]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a refrigerant compressor unit for refrigeration and air conditioning having an oil injection mechanism.

In the closed container 1, a scroll compressor section 2 is provided.
A vertical electric compressor in which the electric motor unit 3 is connected to the upper part and the lower part is accommodated. The compressor section includes both scroll members of a fixed scroll 5 and an orbiting scroll 6 (both wraps of which are reduced for modeling purposes) which form a compression element, a rotation preventing member 6d of the orbiting scroll 6, and A main shaft 7 having a crankshaft 7a that engages with the orbiting scroll 6, and a bearing portion that supports the main shaft 7, that is, a bearing 6c of the orbiting scroll 6 and a main bearing 4 formed on the frame 4.
a, the auxiliary bearing 4b and the like below it. This hermetic scroll compressor is of a high pressure chamber type in which the hermetic container 1 is in an atmosphere of discharge pressure (high pressure side pressure) Pd. The shape of the scroll wrap is an involute or a curve similar to this.

Next, the operation of the scroll compressor will be described according to the flow of the refrigerant gas (the flow of lubricating oil inside the compressor will be omitted). The low temperature low pressure refrigerant gas is
The refrigerant gas introduced from the suction pipe 11 to the suction port 14 in the fixed scroll 5 via the suction joint 12 and the check valve portion 13 as shown by the solid arrow, and the refrigerant gas reaching the compression element portion is introduced into the closed space. It Due to the revolving movement of the orbiting scroll 6 which is prevented from rotating, the compression chamber 8 formed by both scroll members gradually shrinks and moves to the central portion of the scroll, and the pressure of the refrigerant gas is increased so that the refrigerant gas is discharged from the central discharge hole 10. The discharged high-temperature and high-pressure refrigerant gas is discharged into the upper space 1a in the closed container 1 and then the passage 16
The space 1b around the electric motor is filled through a and 16b, and is discharged to the outside through the discharge pipe 18 at a high discharge pressure Pd. The oil injection pipe 21 is connected to the oil injection pores 22 provided in the end plate portion of the fixed scroll 5.

During steady operation of the compressor, the oil supplied through the oil injection pipe 21 is injected into the compression chamber 8 through the pores 22 to cool the working gas in the compression chamber. The oil injected from the oil injection pipe 21 in this way has pores 22.
Is injected into the compression chamber 8 through the above, mixed with the working gas, and discharged together with the working gas from the discharge hole 10 into the discharge chamber 1a. Next, it reaches the electric motor chamber 1b through the passages 16a and 16b, where the working gas and the oil are separated. The separated oil falls and is stored in the lower part of the closed container 1. The working gas having a small oil content reaches the external oil separator 23 through the discharge pipe 18.
Here, the oil in the working gas is separated again, and the oil is supplied as oil for injection through the oil pipes 24, 25. In addition, 2
6 is an oil cooler, and 27 is an oil amount control valve. An oil take-out pipe 28 is provided at the bottom of the container, and the oil pipe 2
8 merges with the oil pipes 24 and 25, and these oil pipes 2
8, 25, 21 and the like make up an oil injection piping path. The solid arrows indicate the flow direction of the working gas (refrigerant gas), and the broken arrows indicate the oil flow direction.

The gas from which oil has been separated by the oil separator 23 is sent to the condenser 30 via the pipe 29. Next, the oil injection pores 22 will be described in detail below. FIG. 2 is a bottom view of the fixed scroll 5 showing the positions of the pores. In the figure, 5e and 5e 'indicate the winding end portions of the fixed scroll wrap 5b. The end face 5g of the fixed scroll wrap has an end face 5g at a substantially central position thereof, and an oil injection fine hole 22 is provided in the end plate 5a.

FIGS. 3 to 5 show the operating state of the compression mechanism using the fixed scroll of the embodiment of FIG. 1 when oil is injected.

In this embodiment, one oil injection hole 22 is provided.
Then, the oil is intermittently injected into the two adjacent compression chambers 8a and 8b. As described above, the compression chambers 8a, 8b and the oil injecting pores 22 are intermittently communicated with each other, thereby providing a function of limiting the amount of lubricating oil (a so-called throttle portion having an adjusting action of the amount of lubricating oil). You can In this case, the pore diameter ds of the pore 22
Is practically satisfied by the following equation with respect to the wrap thickness t of the orbiting scroll.

Ds ≦ t (1) In the case of FIG. 2, the oil injection fine hole 22 is also a position intermittently communicating with the compression working chamber during the suction stroke of both scrolls. This provides a function to prevent oil compression at startup. Further, in FIG. 2, the oil hole 22 temporarily communicates with the compression working chamber during the suction stroke (for example, the space communicating with the suction chamber 5f of 5g and 5g ′ shown in FIG. 3), so that during the suction stroke. The working gas cooling effect is produced, and this also has the effect of improving the volumetric efficiency.

4 and 5, as the orbiting scroll 6 orbits, the oil-injection pores 22 form a compression chamber 8a and a compression chamber 8.
FIG. 7 is an explanatory view for intermittently communicating with b, whereby an oil injection action can be performed intermittently in each compression chamber (be sure to communicate once for one rotation of the main shaft). Two
Reference numeral 1 is a pipe for oil injection.

FIG. 6 shows an oil injection provided at a position closer to the central portion (position where the pressure becomes higher) than the position of the oil injection pore 22 shown in FIG. 2, that is, a position closer to the discharge hole 10. It is an example of the use pore 22b. The pores 22b
Does not communicate with the compression working chamber formed by both scrolls at the time of the suction stroke, but always communicates with the compression chamber 8c or the like that forms a closed space. As described above, the oil injection fine holes 22, 22b are provided at substantially the center position of the tooth bottom surface of the fixed scroll wrap.
The reason for providing is to efficiently distribute the amount of oil supplied to both compression chambers 8a and 8b.

FIG. 7 shows that the end plate portion 5a of the fixed scroll 5 is provided with one oil injection fine hole and the fine hole 22c is provided.
The compression chamber 8a formed by the outer side of the wrap of the fixed scroll 5 and the inner side of the wrap of the orbiting scroll 6, and the compression chambers 8b located at positions substantially symmetrical to the compression chamber 8a have compression chambers 8a, 8b on both sides.
Since it is provided at a position where it is intermittently contacted with the oil, the oil injection pores 22c are located closer to the center of the lap tooth groove than the wrap thickness t from the tooth side surface 5m of the wrap portion of the fixed scroll. This is an embodiment in which holes are provided in the end plate portion of the fixed scroll.

That is, the embodiment of FIGS. 2 to 7 is an embodiment of a structure in which oil is intermittently injected into the two compression chambers 8a and 8b by one injection hole.

8 to 13 show an embodiment in which the diameter of the oil injecting pores is relatively large.

FIGS. 8 and 9 show the oil-injection pores 31 at substantially the center position of the tooth bottom surface 5g of the tooth bottom surface 5a of the end plate portion 5a of the fixed scroll 5 (the central portion of the tooth groove is indicated by a dashed line q). The q curve is also the same as the scroll wrap curve.). The hole 31 includes a narrowed portion 31b and an opening 31a. The diameter of the diaphragm portion 31b is indicated by do. Opening 31
The sectional shape of a is circular, and the hole diameter of the hole 31a is represented by ds. The diameters of these two have a relationship of do <ds so that continuous oil supply (injection) to both compression chambers can be performed.

As shown in FIG. 8, the pores 31 are formed in the compression chamber 8a formed by the wrap outer side of the fixed scroll 5 and the wrap inner side of the orbiting scroll 6, the wrap inner side of the fixed scroll, and the wrap outer side of the orbiting scroll. It is provided at such a position that it communicates with the compression chamber 8b formed at the same time. Therefore, in order to obtain a positional relationship in which the oil injection fine holes 31 (or relatively large oil injection holes) are in constant communication with both compression chambers 8a and 8b, the following equation may be practically satisfied.

T <ds <2ε−t (2) where, t: wrap thickness of orbiting scroll (mm) ε: orbiting radius of orbiting scroll (mm) ds: diameter of oiling hole It is an oil injection pipe, and the direction of oil flow is indicated by a dashed arrow for the sake of explanation.

FIGS. 10 and 11 show another embodiment, in which the oil injection pores 41 provided in the end plate portion 5a of the fixed scroll are
In order to equalize the distribution of the amount of oil supplied to the compression chambers 8a and 8b on both sides formed by both scrolls, a position eccentric to the tooth groove center at a position closer to the outer wall surface 5m 'of the fixed scroll wrap This is an example. In the case of a scroll compressor, the pressure increases toward the center of the scroll, so the internal pressure of the compression chamber 8b is higher than the internal pressure of the compression chamber 8a.

In terms of pressure, it is 18 when displayed by the rotation angle of the spindle.
It is offset by 0 degree (π radian). Therefore, because the differential pressure oil supply is performed with the high-pressure portion that is the supply source, it is necessary to make the oil supply hole 41 longer than the communication period between the oil supply hole 41 and the compression chamber 8a in order to perform pressure distribution evenly. is there. For this reason, the center of the oil supply hole 41 is set at a position closer to the scroll central portion by a distance of ls with respect to the tooth groove center line q, that is, a position eccentric to the tooth groove center. The dimension of ls may be set in consideration of the above formula (1). In practice, l
The dimension of s is roughly expressed by the following equation.

Ls ≈ (1.0 to 2.0) ε / a (3) where, ls: a eccentric amount from the center of the lap tooth groove (mm) ε: turning radius (mm) a: scroll curve In other words, in the embodiment of FIGS. 8 to 11, the oil injection mechanism (or the liquid refrigerant injection mechanism, which is provided in the end plate portion of the fixed scroll, Will be described later.) And one hole (or pore) is provided at a position eccentric to the lap center portion (that is, the scroll lap center portion in the radial direction) from the center position q of the lap tooth groove. The opening of the oil injection hole (compression chambers 5a, 5a, 5
b) is provided.

12 and 13 show another embodiment,
This is an example in which the opening surface of the oil injection fine hole 51 has a long hole shape extending in the radial direction. In this embodiment, the narrowed portion 51b of the oil injection hole 51 connected to the oil injection pipe 21 has a circular shape with a relatively small hole diameter, and the opening 51a engaging with the compression chambers 8a and 8b has a long hole shape. I am trying. In order to set the position of the slot 51a so that the amount of oil supplied to the compression chambers 8a and 8b is evenly distributed, the center p of the slot 51 is set to ls with respect to the tooth groove center line q.
The position is closer to the center of the scroll by the distance.

FIG. 14 shows an operating condition of the compression mechanism using the fixed scroll using the oil injection hole having the long hole shape at the time of oil injection. The dimension Es of the long hole 51 shown in FIG. 8 has a value practically expressed by the following equation.

T <Es <2ε−t (4) In FIG. 14, 5c is a suction hole for the working gas, and 5f is a suction chamber. The working gas is a closed space 8 (8a, 8b, 8) formed by both scroll members 5, 6.
By moving c) from the outside to the center to reduce the volume, the working gas is injected from the central discharge hole 10 provided in the end plate portion of the fixed scroll and is guided to the outside.

In each of the above embodiments, the optimum position structure for the oil injection hole provided in the end plate portion of the fixed scroll is shown.
The present invention is also applied to a refrigerating apparatus using a liquid injection mechanism and a refrigerating apparatus using a gas injection mechanism, and its embodiment will be described below.

FIG. 15 shows an embodiment of a refrigerating apparatus using the liquid injection mechanism of the present invention. Solid arrows indicate the flow direction of the refrigerant gas, and dashed arrows indicate the flow direction of the cooling refrigerant liquid.
The pipes 61 and 62 are liquid refrigerant injection pipes, and the pores 63 provided in the end plate portion 5a of the fixed scroll 5 are the liquid refrigerant injection pores of the present invention. 64 is a condenser, 65 is an evaporator, 66 is a main expansion valve, and 67 is an auxiliary expansion valve. The liquid refrigerant is introduced through the liquid refrigerant injection pipe 61, and the cooling liquid refrigerant is constantly or intermittently injected into both the compression chambers 8a and 8b through the liquid refrigerant injection pores 63. It During the compression process, the injected liquid refrigerant removes the heat of compression (cooling of the refrigerant gas), and eventually serves to cool the entire compressor such as the motor 3. Reference numeral 68 is a check valve for preventing the backflow of the liquid refrigerant and the refrigerant gas from the compression chamber to the sub expansion valve 67. Since the structure of each part of the scroll compressor is the same as that of each of the above-mentioned embodiments, the description thereof will be omitted.

FIG. 16 is a bottom view of the fixed scroll of FIG. 15, showing an embodiment in which the liquid refrigerant injection hole 63 is provided in the end plate portion 5a of the fixed scroll 5. The liquid refrigerant injection hole 63 is
The position is relatively close to the discharge hole 10 provided in the central portion of the fixed scroll. The holes 63 allow the compression chambers 8d, 8
The liquid refrigerant is intermittently injected into d '. As described above, in order to cool the compressor by the liquid injection action, it is desirable to provide the liquid refrigerant injection hole 63 in the final region of the compression stroke (see FIG. 16).

[0031]

The present invention has the following effects. (1) Refrigerant does not flow back to the sub-expansion valve 67 on the liquid refrigerant injection pipe 62 side, and the innermost chamber is several kg / cm ^2.
The pulsating flow of the liquid medium gas and the liquid refrigerant due to the pulsating pressure does not affect the auxiliary expansion valve 67. As a result, the valve operation of the auxiliary expansion valve 67 is stabilized and the malfunction of the auxiliary expansion valve can be eliminated. In addition, the life of the auxiliary expansion valve can be extended.

(2) Since the flow of the liquid refrigerant in the liquid refrigerant injection pipe 62 is a one-way flow, the liquid refrigerant injection pipe 62
Vibration can be reduced.

(3) The phenomenon that the gas refrigerant is mixed into the main refrigerant pipe side can be avoided, and the deterioration of the entire performance of the refrigeration system can be prevented.

(4) The internal volume of the pipe from the liquid refrigerant injection pores to the check valve, the so-called dead volume, is reduced, the internal leakage between the scroll compression chambers is reduced, and the performance of the compressor is improved.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a compressor unit of a refrigerating machine for refrigerating and air conditioning having an oil injection mechanism according to an embodiment of the present invention.

FIG. 2 is a bottom view of the fixed scroll of FIG.

FIG. 3 is a plan view showing a state in which the fixed scroll shown in FIG. 2 meshes with an orbiting scroll.

FIG. 4 is a vertical sectional view of an oil injection mechanism section.

FIG. 5 is a longitudinal sectional view showing the operation thereof.

FIG. 6 is a bottom view of a fixed scroll showing another embodiment in which the positions of oil injection holes are different.

7 is a plan view showing a state in which the fixed scroll shown in FIG. 6 meshes with the orbiting scroll.

FIG. 8 is a vertical cross-sectional view of an oil injection mechanism portion showing still another embodiment.

FIG. 9 is a plan view of an oil injection hole portion.

FIG. 10 is a vertical cross-sectional view of an oil injection mechanism portion showing still another embodiment.

FIG. 11 is a plan view of an oil injection hole portion.

FIG. 12 is a vertical sectional view of an oil injection mechanism showing still another embodiment.

FIG. 13 is a plan view of an oil injection hole portion.

14 is a plan view showing a state in which the fixed scroll shown in FIG. 13 meshes with the orbiting scroll.

FIG. 15 is a configuration diagram of a refrigeration apparatus including a liquid refrigerant injection mechanism showing an embodiment of the present invention.

FIG. 16 is a plan view showing the positions of the liquid refrigerant injection pores in a state where both scrolls are engaged with each other.

[Explanation of symbols]

4 ... Frame, 5 ... Fixed scroll
Reference numeral 5a, 6a ... Scroll end plate portion, 6 ... Revolving scroll, 7 ... Main shaft, 8 ... Compression chamber, 10 ... Discharge hole, 18 ... Communication passage, 61 ... Liquid refrigerant injection pipe, 63 ... Liquid refrigerant Pore for injection, 67 ... Secondary expansion valve, 68
…Check valve.

Claims (3)

(57) [Claims] 1. A refrigeration system provided with a liquid refrigerant injection pipe for introducing a part of the refrigerant liquefied in a condenser of the refrigeration system into a compression chamber of a scroll compressor, wherein a check valve is provided in the liquid refrigerant injection pipe. A refrigerating device characterized by being provided. 2. A refrigerating apparatus having a liquid refrigerant injecting pipe for introducing a part of the refrigerant liquefied in a condenser of the refrigerating device into a compression chamber of a scroll compressor, wherein a sub-expansion valve is provided in the liquid refrigerant injecting pipe. The refrigeration system according to claim 1, further comprising a check valve provided downstream of the auxiliary expansion valve. 3. A refrigeration system provided with a liquid refrigerant injection pipe for introducing a part of the refrigerant liquefied in the condenser of the refrigeration system into the compression chamber of the scroll compressor, in a fixed scroll wrap between the wraps of the tooth bottoms. 2. The refrigerating apparatus according to claim 1, wherein a pore is provided substantially at the center of the liquid, and the pore is connected to the liquid refrigerant injection pipe.