TW201303156A - Reciprocating compressor driven by permanent magnet's linear motor operating at high frequency - Google Patents

Abstract

The present invention relates to a linear compressor which operates at high frequency and is designed to provide an optimization of performance such as to reduce the size of the compressors, besides enabling the operation without the need of using a lubricating oil. It is comprised of a piston (1); a resilient element (2) attached to an axial resilient element (6) of the compressor through a neutral point (3) and cooperating with the piston (1) by means of fastening elements (41) positioned at one of the ends thereof (21); and an motor magnet (5) cooperating with the piston (1) through the resilient element (2), the motor magnet (5) being internal to the resilient element (2) by means of fastening elements (42) positioned on the opposite end (22) of the resilient element (2), and that the operation frequency of the piston (1) / resilient element (2) / motor magnet (5) lies in the range between 200 and 500 Hz, more specifically between 340 and 360 Hz.

Description

Reciprocating compressor driven by a high-frequency permanent magnet linear motor

This invention relates to a linear compressor operating at high frequencies that is designed to optimize performance to reduce device size and to operate without the need for a lubricating oil.

As is known in the art, a compressor is used to increase the pressure of a fluid in a gas state that is widely used in a cooling system, which is basically composed of a piston, an elastic member, and a motor.

In general, the compressors employed in the prior art operate with a motor that cooperates directly with the piston, the elastic member being fastened by one of its side ends and supporting the compression and tensile stresses involved at the opposite ends.

One of the problems typically associated with such devices is that they often involve operating characteristics at low operating frequencies, which results in relatively large compressor sizes, thus giving new aesthetic solutions to devices used with such devices.

For example, it can be cited in document US 2010/0223936, which discloses a linear compressor operating at one of a frequency range between 20 Hz and 200 Hz, but preferably between 40 Hz and 60 Hz. In turn, the compressor disclosed in US 7,185,543 operates at one of the frequencies of 99 Hz, while the document PI 0419019 lists one of the low frequency operating ranges between 30 Hz and 55 Hz.

Document US 2006/0110259 discloses a system for adapting the resonant frequency of a linear compressor to the mass of the resonant device and/or the average frequency of the piston according to the detected operating conditions, although no operational value or possibly maximum frequency achievable is mentioned.

Therefore, it should be noted that the present technology lacks a solution that allows high frequency compressor operation as an efficiency and size optimization. Furthermore, in a similarly known technique, there is often a total energy usage involved in compressor operation. Quite a large electrical loss.

Purpose of the invention

In view of these disadvantages and in order to solve such disadvantages, it is an object of the present invention to provide a reciprocating compressor driven by a linear motor capable of operating at a high frequency.

Another object of the present invention is to provide a compressor that is efficient and reduces in size compared to known similar ones, which makes it possible to reduce the compressor size because of the higher operating frequency.

It is also an object of the present invention to disclose a compressor that operates with low friction and thus is capable of operating without the use of oil as a lubricant.

It is also an object of the present invention to disclose a compressor having a path and frequency that maximizes pumping of the cooling fluid while minimizing electrical losses.

The present invention achieves the above enumerated object by using a reciprocating compressor driven by a linear motor of a permanent magnet operating at a high frequency, the compressor comprising: a piston; an elastic member fastened to the through a neutral point An axial elastic member of the compressor, and cooperating with the piston by a fastening member positioned at one of its ends; and a motor magnet that cooperates with the piston by the elastic member, and the motor magnet utilizes positioning A fastening element at the opposite end of the resilient element reciprocates to the resilient element.

The invention further includes an operating frequency that allows the piston set + elastic element + magnet The rate is maintained in the range of between 200 Hz and 500 Hz (preferably between 300 Hz and 400 Hz, and more specifically between 340 Hz and 360 Hz).

According to a preferred embodiment of the invention, the sum of the masses of the piston and the fastening elements inside one of the ends of the resilient member is between 32 and 50 grams.

Still in accordance with a preferred embodiment of the present invention, the sum of the masses of the piston and the fastening elements inside the end of the resilient member is equal to the sum of the masses of the fastening elements of the motor magnet and the opposite end of the resilient member, acceptable The difference is about 2 grams.

Depending on the operating conditions (evaporation temperature and condensation temperature), the sum of the masses of the piston and the fastening elements inside one of the ends of the elastic element may be a total of the mass of the fastening element inside the opposite end of the motor magnet and the elastic element. The sum is between 5 grams and 20 grams.

Preferably, the spring is made of a metallic material (specifically selected from the group consisting of steel, titanium, and the like).

The invention will be described more fully hereinafter based on the embodiments shown in the drawings.

As can be seen in the drawings shown in Figures 1 and 2, a reciprocating compressor driven by a linear motor of a permanent magnet operating at high frequency, which is the object of the present invention, basically comprises a piston 1, an elastic member 2 and a motor magnet 5 which is fastened to the end 21 of the elastic element via a fastening element 41 while the motor magnet 5 is fastened to the end of the elastic element 2 with the aid of the fastening element 42 22. Thus, in the proposed embodiment, the elastic element is not fastened by one of the side edges of the resilient element, as occurs in the prior art.

In a preferred embodiment of the invention, the resilient member 2 is fastened to the axial resilient member (6) of the compressor through a neutral point 3, which results in the mounting of the piston 1 and the motor in the elastic A lower vibration value is usually configured on the same end of the component 2.

In the illustrated embodiment, the motor magnet 5 is coupled to the piston 1 by an elastic element 2, which is driven from the motor when the elastic element 2 is driven by a periodic current at a natural frequency of the set (not shown) operates to the maximum energy transfer of the piston 1, and depending on the operating conditions (evaporation temperature and condensation temperature), the drive frequency can be increased and should be increased to ensure maximum energy transfer.

According to a preferred embodiment of the present invention, the elastic member 2 (shown in detail in FIG. 3) is a spring made of a metal material (more specifically, an alloy of steel, titanium or the like), when the spring is When one of the ends is supported and experiences one axial displacement of 1 mm at the other end, the spring has a reaction between 160 N and 240 N (specifically, between 190 N and 210 N) force.

The spring or spring element 2 has a natural frequency between 400 Hz and 600 Hz (specifically between 475 Hz and 525 Hz) in the traction-compression mode, ie the deformation of this vibration mode mainly occurs in the shaft In the direction of the orientation, the ends are opposite each other.

Furthermore, the elastic element 2 resists a total axial displacement of 3.4 mm. One half of this displacement is applied to the end of the resilient member 2 during operation of the compressor On the portion 21, the same value is simultaneously applied to the opposite end portions 22, and the directional displacements are also opposed to each other. Since this displacement is applied to the enumerated operating frequency, the minimum number of cycles supported by the elastic element 2 is at least 10 million cycles, for which reason the elastic element 2 should preferably be made of steel, titanium or the like. The alloy is made to exhibit the characteristics of an infinite life of fatigue resistance.

The invention also includes allowing the operating frequency of the piston set 1 + the spring element 2+ motor magnet 5 to be maintained between 200 Hz and 500 Hz (more specifically between 300 Hz and 400 Hz and preferably between 340 Hz and 360 Hz). The components in the scope of).

According to still another preferred embodiment of the present invention, the sum of the masses of the fastening members 41 of the piston 1 and the end portion 21 of the elastic member 2 is in the range of 32 g to 50 g, and the motor magnet 5 is The sum of the masses of the fastening elements 42 inside the end 22 of the resilient element 2 must be equal to the mass of the fastening element 41 of the piston 1 + the end 21 of the resilient element 2, with acceptable tolerances At 2 grams or less than 2 grams.

Depending on the operating conditions (evaporation temperature and condensation temperature), the sum of the masses of the fastening elements 41 of the piston 1 and the end portion 21 of the elastic element 2 may be greater than the total of the motor magnet 5 and the elastic element 2 The sum of the masses of the fastening elements 42 inside the end 22 is greater than a value between 5 grams and 20 grams.

It is worth mentioning that the piston 1 and the motor magnet 5 are mounted on the opposite axial ends 21, 22 of the resilient element 2 (which can be a coil spring).

When in operation, the set of motor magnets 5+piston 1+elastic elements 2 function in a natural vibration mode wherein the periodic axial movement of the motor and piston 1 provides between 170 and 190 degrees (preferably, One phase difference between 175 degrees and 185 degrees). Under these conditions, the natural vibration frequency is between 200 Hz and Between 500 Hz (specifically, between 300 Hz and 400 Hz), this frequency is often referred to as the operating frequency and the efficiency and final size of the compressor is determined based on this operating frequency. The compressor is constructed from a preferred embodiment in accordance with a preferred embodiment of the present invention having a desired range of between 340 Hz and 360 Hz, which constitutes a 200 watt capacity and an optimum point for a device volume that is as small as possible.

In short, the mass and stiffness properties of the group are characterized by a compressor that maximizes the pumping of the cooling fluid and the path and frequency of compressor performance.

Therefore, the unique feature of the present invention is that the operation at high frequency results in a reduction in the size and mass of the compressor; since the machining is one of the final processes, the geometric accuracy is relatively high and the change in stiffness is reduced; The fatigue resistance is increased by heat treatment and "bead strike"; the piston assembly 1 + the fastening assembly 41 at one end 21 of the elastic member 2 and the fastening assembly at the other end 22 of the motor magnet 5 + 42. The fastening of the elastic element 2 to the axial elastic element (6) through the "neutral point" results in a normal group than mounting the piston and the motor on the same end of the elastic member. The lower vibration value; and the quality of the piston + fastening is similar to the quality of the motor magnet + fastening provides the highest natural frequency and therefore can be operated. Depending on the operating conditions (evaporation temperature and condensation temperature), it is necessary to reduce the mass of the magnet side and/or increase the mass of the piston side in order to maintain the natural frequency system the maximum possible frequency.

It is also apparent that all combinations of elements that perform the same function in substantially the same manner to achieve the same result are within the scope of the invention. Also completely hope and The use of other elements in place of a component of the described embodiments is contemplated.

However, it should be understood that the above description based on the above figures is only relevant to one of the possible embodiments of the system of the present invention, and the actual scope of the object of the present invention is defined in the scope of the accompanying claims.

1‧‧‧Piston

2‧‧‧Flexible components

3‧‧‧Neutral point

5‧‧‧Motor magnet

6‧‧‧Axial elastic elements

21‧‧‧ End

22‧‧‧ End

41‧‧‧ fastening elements

42‧‧‧ fastening elements

1 shows an exploded perspective view of an assembly of a compressor constructed in accordance with a preferred embodiment of the present invention.

Figure 2 shows a longitudinal section view of one of the compressors illustrated in Figure 1 that is suitably assembled and ready for use.

Figures 3.1 and 3.2 show, respectively, a front view and a perspective view of a possible embodiment of the use of a resilient member for the compressor shown in Figure 1.

Figures 4.1 and 4.2 show a possible embodiment of a fastening element to the neutral point of the elastic element of the outer casing in a front view and a perspective view.

Figures 5.1 and 5.2 show a further embodiment of the fastening element to the neutral point of the elastic element of the outer casing in a front view and a perspective view.

1‧‧‧Piston

2‧‧‧Flexible components

3‧‧‧Neutral point

5‧‧‧Motor magnet

6‧‧‧Axial elastic elements

21‧‧‧ End

22‧‧‧ End

41‧‧‧ fastening elements

42‧‧‧ fastening elements

Claims (8)

A reciprocating compressor driven by a linear motor driven by a high frequency permanent magnet, characterized in that it comprises: a piston (1); an elastic member (2) attached to the compression through a neutral point (3) An axial elastic element (6), the elastic element (2) cooperating with the piston (1) by a fastening element (41) positioned at one of its ends (21); and a motor magnet (5) cooperating with the piston (1) through the elastic element (2), the motor magnet (5) utilizing a fastening element (42) positioned on the opposite end (22) of the elastic element (2) Located inside the elastic member (2), the operating frequency of the piston (1) / elastic member (2) / motor magnet (5) is maintained in a range between 200 Hz and 500 Hz. The compressor of claim 1, wherein the piston group (1) / elastic member (2) / motor magnet (5) operates at a frequency between 300 Hz and 400 Hz. The compressor of claims 1 and 2, wherein the piston group (1) / elastic member (2) / motor magnet (5) operates at a frequency between 340 Hz and 360 Hz. The compressor of claim 1, wherein the sum of the masses of the piston (1) and the fastening members (41) inside the end portion (21) of the elastic member (2) is from 32 g to 50 g. In the scope. The compressor of claim 4, wherein the sum of the masses of the piston (1) and the fastening members (41) inside the end portion (21) of the elastic member (2) is equal to the motor magnet (5) and The sum of the masses of the fastening elements (42) inside the end portion (22) of the elastic member (2) has a tolerance of more than 2 grams or less than 2 grams. The compressor of claims 4 and 5, wherein the sum of the masses of the piston (1) and the fastening elements (41) inside the end portion (21) of the elastic member (2) is greater than the motor magnet ( 5) The sum of the masses of the fastening elements (42) inside the end portion (22) of the elastic member (2) is greater than a value between 5 grams and 20 grams. A compressor according to claim 1, wherein the elastic member (2) is a spring made of a metal material. The compressor of claim 7, wherein the material from which the elastic member (2) is made is selected from the group consisting of alloys of steel, titanium, and the like.