KR100944110B1 - Vertical piston equipped the reciprocating compressor - Google Patents

Abstract

PURPOSE: A reciprocating compressor with a vertical piston is provided to minimize the vibration factor perpendicular to a crank shaft because the piston reciprocates on the same line as the rotary axis of the crank shaft. CONSTITUTION: A reciprocating compressor comprises an electric motor which rotates a crank shaft(1) and a piston(2) which converts the rotation of the crank shaft to linear motion so as to compress refrigerant. A constrained member(6) is projected on the inner surface of a compression chamber(4) surrounding the piston. A transfer groove(21) of continuous curved shape is formed on the outer surface of the piston to make the piston reciprocate when the crank shaft rotates.

Description

Reciprocating compressor with vertical piston

The present invention relates to a reciprocating compressor having a piston for converting the rotation of the crankshaft into a linear motion, and more particularly to a reciprocating compressor having a vertical piston which reduces the noise and vibration by causing the piston to reciprocate on the rotating shaft of the crankshaft. .

The compressor compresses the heating medium during the four processes of air conditioning cycle, condensation, expansion, and evaporation, that is, converts the heating medium into a gaseous heating medium of high temperature and high pressure and sends it to the next step. Accordingly, it is divided into a volume compression type, ie, a reciprocating compressor, a screw compressor, a rotary compressor, and a centrifugal turbo compressor.

The compressor is classified into an open type, a closed type, and a semi-sealed type according to its appearance, and is classified into a water cooling type and an air cooling type by a cooling method, classified into low, medium, and high speed according to the rotational speed, and classified into a short passage and a multi cylinder by the number of cylinders. .

Among the compressors divided into various forms as described above, in the present application, a sealed reciprocating compressor will be described as an example as shown in FIGS. 10 to 12. The electric motor and the compressor are sealed by the upper case 51 and the lower case 52. The inside of the main body frame 55, which is supported by the support bar 54 by the compression spring 53 or the leaf spring for the purpose of proper dustproof and soundproof means is built.

The main body frame 55 is capable of reciprocating the cylinder block 58 and the cylinder 58a therein to the upper end of the crankshaft 57 to which the motor unit 56 having the stator and the rotor are fixed. The piston 59 is provided, and the suction and discharge valve bodies 60 provided at the left end of the cylinder block 58 are installed by the reciprocating motion of the piston 59 to inhale low pressure and low temperature refrigerant gas, High temperature refrigerant gas is discharged.

The suction and discharge valve body 60 is composed of a flapper or lead type thin plate structure which is usually elastic for miniaturization, and the flapper or lead type suction and discharge valve body 60 is double-sided. It is opened and closed passively by the pressure difference acting on.

The sealed reciprocating compressor 50 configured as described above has a suction pipe 61 and a suction muffler fixed to the lower pressure / low temperature refrigerant gas to be sealed to the upper or lower cases 51 and 52 during the backward movement of the piston 59. 62 is introduced into the suction chamber of the discharge muffler 64 from the external evaporator (not shown) to the suction lead valve of the suction and discharge valve body 60, and then flows into the cylinder 58a and the piston 59. During the forward movement of the high-pressure and high-temperature refrigerant gas discharged from the compressor is passed through the discharge muffler 64 from the discharge valve of the suction and discharge valve body 60 to the upper or lower case 51 and 52. It is sent to an external condenser (not shown) via the discharge tube 65 fixedly sealed. Here, reference numeral 67 is fixed to the lower case 52 by a refrigerant filling pipe and is initially sealed after filling the refrigerant gas inside.

The noise of the hermetic reciprocating compressor 50 is generated by the reciprocating motion of the piston 59, the opening and closing shock of the suction and discharge valve body 60, the pulsation of the suction gas and the discharge pressure, and the like. In order to reduce noise caused by the pulsation of the suction and discharge pressure, the refrigerant gas introduced into the suction pipe 61 is discharged through the suction muffler 62 while being filled in the upper and lower cases 51 and 52. ) Is sucked into the cylinder (58a) through the suction chamber, and the refrigerant compressed in the cylinder (58a) is discharged to the discharge tube (65) through the first discharge chamber and the second discharge chamber of the discharge muffler (64).

On the other hand, the motor portion 56 is composed of a stator 68 is fixed to the lower portion of the body frame 55 and a rotor 69 that rotates with a gap between the stator 68, this rotor 69 ) Is rotatably supported on the body frame 55 to be fixed to the crankshaft 57 and rotate together.

At the end of the crankshaft 57 of the electric motor unit 56, an eccentric shaft 57a is formed to protrude upward from the main body frame 55 so that the piston 59 is the piston rod 59a and the eccentric shaft thereof. By connecting to 57a, the piston 59 reciprocates by the amount of eccentric rotation of the eccentric shaft 57a. In addition, an external power source is applied to the winding coil of the stator 68 of the motor unit 56 by installing external terminals 70 which are hermetically fixed to the upper and lower cases 51 and 52.

In order to smoothly operate the compressor and the driving motor operated as described above, a coolant oil storage tank 52a for storing coolant oil is formed at the bottom of the lower case 52 along the lubricating oil supply groove 57b of the crankshaft 57. While being sucked to the top, the refrigerant oil was supplied to each lubrication part to enable lubrication.

As shown in FIG. 12, the piston 59 reciprocating in the cylinder 58a is supported at the inner end of the piston 59 by the coupling hole 59a 'formed as one end of the piston rod 59a. The member 592 is engaged by line contact with the engaging portion 590 provided.

The support member 592 installed at the inlet portion of the coupling portion 590 smoothly flows when the coupling hole 59a 'flows left and right in the coupling portion 590 during the reciprocating movement of the piston 59. It was installed to make it possible.

In order to obtain the linear movement of the piston 59 by the rotational movement of the crankshaft 57, the eccentric shaft 57a was used so that the rotational axis of the crankshaft 57 and the reciprocating direction of the piston 59 were perpendicular to each other. At this time, the eccentric shaft (57a) is made of a cam member (57b) that the piston rod is rotatably coupled to the crank shaft and the rotating shaft, the problem that the large vibration is caused to the cam member during rotation of the eccentric shaft (57a) have. In order to reduce the vibration of the cam member (57b) attempts to balance the weight by forming a large opposite side of the one side to which the piston rod is coupled, there is still vibration even when using such an atypical cam member.

In addition, the vibration of the cam member occurs in a direction perpendicular to the crank shaft to rotate at high speed, adversely affects the durability of the motor portion, there is also a problem that the vibration is gradually increased due to a large wear on the motor portion after long use.

On the other hand, due to the repeated friction between the coupling portion (53a ') and the support member 592 during the reciprocating motion of the piston, there is a problem that the life is shortened. Therefore, in order to maintain sufficient rigidity in the support member, there is also a problem in that the manufacturing cost increases due to the strict manufacturing tolerances and, in certain cases, additional lubrication means.

In addition, by mechanically connecting the cam member, the piston rod, and the piston to the crankshaft, the frictional part is increased, which also has the disadvantage of increasing the operating noise. As the service life increases, wear increases and the operating noise gradually increases. When the compressor is used in household appliances, the consumer reacts sensitively to the increase of the small noise, so it is necessary to maintain a quiet operation noise for a long time.

The present invention has been made to solve the above-described problem, an embodiment of the present invention has the object of causing the piston to reciprocate on the rotation axis of the crankshaft.

In addition, it has the purpose of reducing the magnitude of the force required to compress the refrigerant by the piston, so that the compression of the refrigerant can be efficiently performed even with a small force.

It also has the purpose of allowing the number of compression times to vary according to the rotation of the crankshaft.

In order to solve the above problems, the present invention is a reciprocating compressor including an electric motor unit for rotating the crankshaft, and a piston for compressing the refrigerant by converting the rotational force of the crankshaft in a linear motion, the piston of the crankshaft A reciprocating compressor provided with a vertical piston is characterized by linear reciprocating motion on the same axis as the rotating shaft.

In addition, the piston proposes a reciprocating compressor equipped with a vertical piston, characterized in that the linear reciprocating motion while rotating.

In addition, a constrained body is formed on the inner circumferential surface of the compression chamber surrounding the piston, the outer circumferential surface of the piston is constrained to the constrained body is characterized in that the feed groove for linear movement of the piston when the crankshaft is formed A reciprocating compressor with a vertical piston is presented.

In addition, the conveying groove has a height difference between the maximum height value and the minimum height value on the outer peripheral surface of the piston proposes a reciprocating compressor having a vertical piston, characterized in that formed in a continuous curve.

In addition, the maximum height value and the minimum height value presents a reciprocating compressor with a vertical piston, characterized in that the plurality is formed sequentially.

In addition, the conveying groove provides a reciprocating compressor with a vertical piston, characterized in that formed in a pair of curves symmetrically up and down at the middle height between the maximum height value and the minimum height value.

In addition, the restraint member presents a reciprocating compressor with a vertical piston, characterized in that the pair is installed symmetrically to each other on the axis passing through the center of the cross section of the compression chamber.

In addition, the conveying groove proposes a reciprocating compressor having a vertical piston, characterized in that a plurality is provided in parallel in the vertical direction of the piston.

In addition, the restraining body for restraining each of the conveying grooves is presented a reciprocating compressor with a vertical piston, characterized in that formed radially on the outer surface of the compression chamber.

In addition, there is also an object to make the vertical movement of the piston in a stable manner.

According to the reciprocating compressor with a vertical piston according to the embodiment of the present invention as described above, as the reciprocating motion of the crankshaft rotational axis and the piston is in the same line, the entire compressor by reducing the vibration component in the vertical direction of the crankshaft to a minimum Its vibration characteristics are improved, and the number of components required for converting the crankshaft to the linear movement of the piston is reduced, thereby minimizing the friction part, thereby reducing the operating noise. In addition, compared with the prior art, the size of the upper part of the main body plate can be made small, and the compressor can be made small.

Specifically, since the configuration of the conventional cam member and the piston rod is replaced by a conveying groove integrally formed on the outer peripheral surface of the restraint body and the piston, the vibration element is reduced, and the occurrence of noise is significantly reduced.

In addition, since the rotation of the crankshaft is directly switched to the linear motion of the piston, the rotational energy of the crankshaft is converted into the linear motion with high efficiency, thereby increasing the energy efficiency.

In addition, since the piston rotates linearly, the size of the force required to compress the refrigerant by the piston is reduced, so that the refrigerant can be efficiently compressed even with a small force, thereby enabling the installation of an electric motor having a small power consumption. .

On the other hand, when a plurality of feed grooves are provided in the piston, a restraint body supporting each feed groove may be disposed radially, so that the outer circumferential surface of the piston may be stably held, thereby improving the operational reliability of the compressor.

Hereinafter, the preferred embodiment of the accompanying drawings, the function, configuration and operation of the reciprocating compressor with a vertical piston of the present invention will be described in detail.

1 is a cross-sectional view of an essential part of a reciprocating compressor with a vertical piston according to a first embodiment of the present invention, Figure 2 shows a piston employed in the present invention, (a) is a perspective view, (b) is It is an exploded view of the conveying groove formed in the outer surface.

In the reciprocating compressor 100 provided with the vertical piston according to the first embodiment of the present invention, an electric motor part (not shown) for rotating a crankshaft and a rotational force of the crankshaft 1 are installed above the motor part. Compression chamber (4) for compressing the refrigerant through the piston (2) linear movement using the is provided.

At this time, the motor portion is made of a motor having a known configuration to rotate the crank shaft (1) in the vertical direction, this motor portion is coupled to the lower portion of the main frame 3 so that the crank shaft (1) protrudes.

On the other hand, the compression chamber 4 is formed inside the block body 4a which is settled on the upper part of the protruding main body frame 3 of the crankshaft 1. The compression chamber 4 is formed of a cylindrical hole elongated in the vertical direction to become a cylinder for linear movement of the piston 2 in the vertical direction. In the upper part of the compression chamber 4, the suction and discharge valve bodies 5 for compressing the refrigerant are connected in communication.

At this time, the intake and discharge valve body 5 has a known configuration, and is composed of a flapper or reed type thin plate structure having a generally elasticity, and the flapper or lead type intake and discharge valve body. Is passively opened and closed by a pressure difference acting on both sides.

At this time, the rotation of the crankshaft (1) is converted into a linear motion in the vertical direction by the restraining body 6 protruding from the inner wall surface of the compression chamber 4 and the conveying groove 21 formed on the outer peripheral surface of the piston (2) , The piston (2) is a linear reciprocating motion on the same axis as the rotation axis of the crankshaft (1).

As a result, the inner volume of the compression chamber 4 is changed by the vertical reciprocating motion of the piston 2 provided in the compression chamber 4, and the suction and discharge valve bodies 5 are passively driven by the pressure difference. It opens and closes and the refrigerant can be compressed.

In this case, as both the rotational axis of the crankshaft and the linear movement direction of the piston are made on the same axis, the vibration direction of the compressor by the piston occurs in the up and down direction of the crankshaft. Therefore, unlike the prior art, the vibration component in the vertical direction of the crankshaft is minimized to have an effect of improving the vibration characteristics of the entire compressor. In addition, the vibration characteristics are improved, and at the same time, the number of components required to convert the crankshaft rotation into the linear movement of the piston can be reduced, thereby minimizing the friction part, thereby reducing operating noise. Furthermore, compared with the prior art, the size of the upper part of the main body frame can be made small, and the compressor can be made smaller.

The configuration of switching the rotation of the crankshaft 1 to the linear movement of the piston 2 will be described in detail as follows.

As shown in FIG. 1, the restraint body 6 is provided in a hole 41 formed in the inner wall of the compression chamber 4, and is supported by the elastic means 61 in the hole 41 and compressed. It consists of a support ball 62 protruding toward the inner wall surface of the seal (4). At this time, the support 63 for pressing the support ball in the plane may be further coupled between the elastic means 61 made of a spring and the support ball 62 so that the support ball 62 rotates smoothly.

On the other hand, on the outer circumferential surface of the piston 2, as shown in FIG.

The support ball 62 protruding from the inner circumferential surface of the compression chamber 4 is applied to the recessed conveying groove 21, and when the piston 2 is rotated, the support ball 62 rides on the trajectory of the conveying groove 21. Accordingly, the piston moves linearly in the vertical direction.

Figure 3 is a perspective view schematically showing the operating relationship between the piston and the crankshaft employed in the present invention, a configuration in which the rotational force of the crankshaft is transmitted to the piston.

The crankshaft (1) is provided in the motor portion, it is rotated but does not move in the vertical direction. The upper end 11 of the crankshaft (1) protruding from the main frame has a polygonal cross section, and the lower end of the piston (2) is fitted into the polygonal cross section so that the upper end (11) of the crankshaft (1) is inserted ( 22 is formed, the upper end portion 11 of the crankshaft 1 is coupled to the fitting groove 22 so as to be slidable in the vertical direction. As a result, the rotational force of the crankshaft is transmitted to the piston without loss, and the piston can move in the up and down direction of the crankshaft by the above-described relation between the restraint and the transfer groove.

At this time, a lubrication hole 12 is formed in the center of the crankshaft so as to smoothly slide between the upper end portion 11 of the crankshaft 1 and the fitting groove 22 of the piston 2, and the lubrication hole 12 It may have a configuration to continuously inject lubricating oil into. It is also possible to install a bearing on the contact surface of the crankshaft and the piston for sliding in the vertical direction.

In this case, while the piston is rotated by the crankshaft, the piston can linearly reciprocate in the compression chamber, thereby increasing the compression efficiency of the piston. That is, since the piston is a combination of the rotational movement and the upward movement, it is possible to compress the refrigerant more efficiently with less rotational force than in the prior art that the piston is only a simple linear motion. Therefore, it is possible to reduce the power consumption of the electric motor portion made of an electric motor.

Referring to FIG. 2 again, in order to obtain a proper linear motion of the piston in the rotation of the crankshaft (1), the conveying groove 21 is the maximum height value 211 and the minimum height value (on the outer circumferential surface of the piston 2) The height difference H of 212 may be formed in a continuous curve.

At this time, the height difference between the maximum height value 211 and the minimum height value 212 of the transfer groove 21 in the trajectory of the transfer groove 21 shown in (b) of Figure 2 and the bottom dead center of the piston (2) It is the height difference of top dead center. Therefore, by adjusting the height difference between the maximum height value and the minimum height value in the formation of the conveying groove, it is possible to control the volume change of the pressure chamber during one rotation of the piston. In addition, the inclination of the trajectory of the transport groove due to the diameter of the piston and the height difference can be reduced to further control the compression force of the piston.

Hereinafter, the operation relationship between the piston and the crankshaft employed in the present invention will be described with reference to FIG. 4. 4A is a cross-sectional view of the top dead center of the piston 2, and corresponds to a case where the restraint body 6 is caught at a position corresponding to the minimum height value of the transfer groove 21.

Then, when the crankshaft 1 is rotated 90 degrees from the right side to the left side of the figure, as shown in (b) of FIG. In this case, the piston 2 is also rotated and lowered by the rotational angle of the crankshaft 1 to increase the volume of the compression chamber.

After the crankshaft 1 is rotated further and rotated 108 degrees from the beginning, as shown in FIG. 4C, the restraint member 6 is caught in a position corresponding to the maximum height value of the transfer groove 21. do. At this time, the piston (2) is rotated with the crankshaft (1) and further lowered and positioned at the bottom dead center, the volume of the compression chamber is the maximum.

As the crankshaft is further rotated, the restraints are sequentially caught in the downward curved portion of the trajectory of the feed groove and the piston is raised. In this way, the rotational speed of the crankshaft and the rotational speed of the piston are made the same, and during one rotation of the crankshaft, the piston is made one up and one down.

On the other hand, Figure 5 shows a piston employed in the reciprocating compressor with a vertical piston according to the second embodiment of the present invention, (a) is a perspective view, (b) is an exploded view of the transfer groove formed on the outer surface. .

The reciprocating compressor equipped with the vertical piston according to the second embodiment of the present invention has the same configuration as the first embodiment except for the feed groove 21 of the piston 2. Hereinafter, the transfer groove of the vertical piston according to the second embodiment and the working relationship thereof will be described, and descriptions of other components will be omitted since they overlap.

The maximum height value 211 and the minimum height value 212 are sequentially formed in the feed groove 21 of the piston 2 provided in the second embodiment of the present invention. 5 illustrates a case where the maximum height value 211 and the minimum height value 212 are sequentially repeated twice in the transfer groove 21.

In this case, when the crankshaft is rotated once by the feed groove 21 restrained by the restraint body 6, the vertical movement of the piston 2 is made twice. If the maximum height value and the minimum height value of the feed groove are sequentially formed a plurality of times, the vertical movement of the piston per one revolution of the crankshaft is repeatedly performed as many times as the repeated number.

As described above, as the maximum height value and the minimum height value of the transfer groove are formed in plural, fast compression of the refrigerant may be obtained while having an electric motor unit having the same rotation speed. Therefore, in a compressor equipped with an electric motor having a large torque instead of a low rotation speed, high efficiency can be obtained by providing a piston as in the second embodiment of the present invention.

Figure 6 shows a piston employed in the reciprocating compressor with a vertical piston according to the third embodiment of the present invention, (a) is a perspective view, (b) is an exploded view of the transfer groove formed on the outer surface, 7 is a cross-sectional view showing a coupling relationship of the reciprocating compressor with a vertical piston shown in FIG.

The reciprocating compressor with the vertical piston according to the third embodiment of the present invention has the same configuration as the first embodiment except for the following description, and duplicated description is omitted.

The conveying groove 21 formed on the outer circumferential surface of the piston 2 according to the third embodiment is formed as a pair of curves symmetrically up and down at the middle height between the maximum height value 211 and the minimum height value 212. At this time, the intersection of the transfer groove formed at the intermediate height is preferably formed to be orthogonal in the progress direction of each trajectory.

In addition, as shown in FIG. 7, a pair of restraints 6 protruding from the inner circumferential surface of the compression chamber 4 are symmetrically disposed on an axis passing through the center of the cross section of the compression chamber 4, and each of the transfer grooves 21 is provided. To bind. At this time, the conveying groove 21 supported by any one of the restraint member 6 during the ascending or descending movement of the piston 2 is continuous past the intersection point of the conveying groove by the inertia of the rotating and rising or lowering piston. It is moved to the transfer groove. Therefore, any one constrainer will constrain the same transfer groove continuously.

In this case, since the restraints provided symmetrically to each other are configured to restrain both sides of the piston, that is, both sides of the conveying groove, the piston can be restrained more stably during the rapid vertical movement of the piston. Therefore, even if there is some wear on the conveying groove by long time use, the operation of the piston is guaranteed to have a long service life.

In addition, as compared with the fourth embodiment to be described later, since the double feed groove is formed at the same height, there is also an advantage that does not need to elongate the vertical length of the piston. In other words, it is possible to secure the stability of the piston operation without extending the vertical height of the piston.

On the other hand, Figure 8 shows a piston employed in the reciprocating compressor with a vertical piston according to a fourth embodiment of the present invention, (a) is a perspective view, (b) is an exploded view of the transfer groove formed on the outer surface 9 is a cross-sectional view illustrating a coupling relationship of a reciprocating compressor having a vertical piston illustrated in FIG. 6.

The reciprocating compressor equipped with the vertical piston according to the fourth embodiment of the present invention has the same configuration as the first embodiment except for the following description, and duplicated description is omitted.

The transfer groove 21 is provided with a plurality in parallel in the vertical direction of the piston (2). In addition, the restraining body restraining each of the conveying grooves 21 is provided radially on the outer surface of the compression chamber.

At this time, the plurality of transfer grooves 21 formed on the outer circumferential surface of the piston (2) is formed equally spaced apart from each other, as shown in Figure 8 (b), the trajectory by each transfer groove 21 Up and down parallel. Therefore, the spacing of the feed grooves 21 is kept constant on either side of the piston 2.

Meanwhile, a plurality of restraints 6 protruding from the compression chamber 4 are provided according to the number of the transfer grooves 21, and each restraint member 6 restrains one of the transfer grooves 21. will be.

Such a restrictor may be formed in a straight line in the vertical direction. At this time, the spacing of the constraint is the same as the spacing of the conveying groove.

More preferably, each of the restraints 6 is radially formed to spread at an equal angle from the center of the compression chamber 4. At this time, the forming height of each of the restraints 6 is formed in accordance with the height of the trajectory of each conveying groove 21 of the piston 2, so that one restraint 6 is installed to support one conveying groove 21. will be. As an example, when the transfer groove is formed in three, the restraint body is disposed at 120 degree intervals to support the piston evenly, and as shown in the case in which the transfer groove 21 is formed in two, as shown in FIG. 9. As it is arranged at intervals of 180 degrees to be able to support both sides of the piston 2 evenly.

As a result, as in the above-described third embodiment, the support of the piston is made to be stable, thereby improving the operation reliability of the piston.

In the reciprocating compressor having a vertical piston according to embodiments of the present invention, the cam member and the piston member employed in the related art may be omitted. Therefore, as the component is reduced, noise due to friction can be reduced, and energy efficiency is increased by switching to linear movement of the piston while minimizing the loss of rotational energy of the crankshaft. In addition, since the direction of rotation of the piston and the direction of rotation of the crankshaft are the same, the vibration component in the direction perpendicular to the crankshaft is remarkably reduced as in the prior art. Therefore, even in the case of using the electric motor for a long time, it is also possible to reduce the wear caused by the vibration transmitted in the direction of the rotation axis and the vertical direction, so that long-term quiet operation is possible.

1 is a cross-sectional view of an essential part of a reciprocating compressor having a vertical piston according to a first embodiment of the present invention.

Figure 2 shows a piston employed in the present invention, (a) is a perspective view, (b) is an exploded view of the transfer groove formed on the outer surface.

Figure 3 is a perspective view schematically showing the operating relationship between the piston and the crankshaft employed in the present invention.

Figure 4 shows the operating relationship between the piston and the crankshaft employed in the present invention in sequence, (a) is a cross-sectional view of the top dead center of the piston, (b) is a cross-sectional view of the middle point of the piston, (c) is a bottom dead center of the piston Section.

Figure 5 shows a piston employed in the reciprocating compressor with a vertical piston according to a second embodiment of the present invention, (a) is a perspective view, (b) is an exploded view of the transfer groove formed on the outer surface.

Figure 6 shows a piston employed in the reciprocating compressor with a vertical piston according to a third embodiment of the present invention, (a) is a perspective view, (b) is an exploded view of the transfer groove formed on the outer surface.

7 is a cross-sectional view showing a coupling relationship of the reciprocating compressor with a vertical piston shown in FIG.

Figure 8 shows a piston employed in the reciprocating compressor with a vertical piston according to a fourth embodiment of the present invention, (a) is a perspective view, (b) is an exploded view of the transfer groove formed on the outer surface.

9 is a cross-sectional view showing the coupling relationship of the reciprocating compressor with a vertical piston shown in FIG.

10 is a plan view of essential parts of a conventional technology.

11 is a side cross-sectional view of the prior art.

12 is a plan view of a piston and a cam member employed in the prior art.

Explanation of symbols on the main parts of the drawings

100: compressor

1: crankshaft

11: upper part 12: lubrication hole

2: piston

21: feed groove 211: maximum height value 212: minimum height value H: height difference

213: intermediate point 22: fitting groove

3: main frame

4: compression chamber 4a: block

41: hall

5: suction and discharge valve body

6: constraint

61 elastic means 62 support ball 63 support

Claims (9)

delete delete delete delete In the reciprocating compressor including an electric motor portion for rotating the crankshaft (1), and a piston (2) for converting the rotation of the crankshaft (1) into linear motion to compress the refrigerant, Constraints 6 protruding from the inner circumferential surface of the compression chamber 4 surrounding the piston 2 is formed, A maximum height value 211 is provided on the outer circumferential surface of the piston 2 so that the outer circumferential surface of the piston 2 is constrained to the restraint member 6 so that the piston 2 linearly moves when the crankshaft 1 rotates. ) Has a height difference (H) between the minimum height value 212 and the transfer groove 21 is formed in a continuous curve, The maximum height value (211) and the minimum height value (212) of the conveying groove 21 is a reciprocating compressor with a vertical piston, characterized in that the plurality is formed sequentially. In claim 5, The transfer groove 21 is Reciprocating compressor provided with a vertical piston, characterized in that formed in a pair of curves symmetrically up and down at the middle height between the maximum height value 211 and the minimum height value (212). In claim 6, The restraint body is a reciprocating compressor having a vertical piston, characterized in that the pair is installed symmetrically to each other on the axis passing through the center of the cross section of the compression chamber. In claim 5, The transfer groove 21 is Reciprocating compressor provided with a vertical piston, characterized in that a plurality is provided in parallel in the vertical direction of the piston. In claim 8, The restraining body restraining each of the transfer grooves 21 Reciprocating compressor provided with a vertical piston, characterized in that provided radially on the outer surface of the compression chamber.

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