How to respond to complaints Essay Example for Free

How to respond to complaints Essay Always follow the settings procedure policy when dealing with complaints. Complaints may be telephoned in, emailed or in person and there will be a different protocol and timescale to follow. When dealing with a complaint face to face keep calm and listen. The person complaining may be angry and I need to stay calm ensure they can see I’m listening and never raise my voice and avoid it escalating. If the discussion is infront of others try to move it somewhere that is more confidential, trying to move the discussion may also help if the person is very angry or upset. Gives them a couple of minutes to calm down while you re-locate. Always show that you’re listening and giving them your whole attention, never look dismissive. Reflect back on what they’ve said repeating back key points so they can hear you’ve understood and listened to what they’ve said. It also helps highlight if I’ve misunderstood a point so they can correct me. Always apologise if I am in in the wrong, misunderstood or forgotten an instruction. Explain what actions I can take to correct the situation. For example a parent asked me to not give their child any sweet foods. Another child had brought in a cake for their birthday and I had forgot to write the parents wish on the board, leading to the child eating some cake. I could apologise, admit fault and ensure the parent that the notice would instantly be placed on the appropriate board. The next day when they dropped the child off I could have a private talk with the parent/carer and show that it is now on the board and I did follow up and correct the mistake. In some cases an explanation or apology will not resolve the situation. Discuss a compromise that suits everybody to bring out a win/win solution. The main thing when dealing with complaints is to stay calm, listen and to be tactful, don’t make any personal comments that may cause the situation to escalate. Choose my words wisely and think before I speak.

PHILADELPHIA, HERE I COME! :: English Literature

PHILADELPHIA, HERE I COME! A young prospective man called Gar O 'Donnell is the centre point of the book 'Philadelphia Here I Come'. The action takes place the night before and the morning of Gar's departure for Philadelphia. Gar lives in a small village in County Donegal called Ballybeg. Gar finds his home life very boring and repetitive. Through out the book Gar shows his feelings about the village by what he says and does. "Aye, and but for Aunt Lezzy and the grace of God, you'd be there tonight, too, watching the lights go out over the village, and hearing the front doors being bolted, and seeing the blinds being raised; and you stamping your feet to keep the numbness from spreading, not wanting to go home, not yet for another while, wanting to hold on to the night although nothing can happen now, nothing at allà ¢Ã¢â€š ¬Ã‚ ¦". This is one example were Gar shows his realistic views. The book was set in the 1960's, and at this time Ireland was a lot different than it is today. There was a lot of Irish emigrating to nearer countries to live a new life. One reason for this was because the Irish economy was in a depressed state. The people of Ballybeg were slaves of routine, and they had very little to do in such a small community. Gar soon realises that he will never be able to live an exciting life in Ballybeg and soon recognizes that he has no future in his home village. This leads to Gar deciding to move to Philadelphia, where he hopes life has a better impact on his future. There are many reasons for Gar wanting to leave Ballybeg. Gars life has been a very emotional time. Gars mother died shortly after his birth, this was a huge upset for him and his father. To make things worst Gar's father, S.B, does not get on with his only son, even know Gar lives and works with him. They see each other every day and still their communication levels are low. ''If he wants to speak to me he knows where to find me! But I'm damned if I'm going to speak to him first''. This is one example of were Gar gets so annoyed he starts to take it out on poor Madge who is trying to help. Gar doesn't mean to but it is he is so annoyed at the sate of his life. They only communicate when essential. Gar is leaving for Philadelphia in the morning, and still his father does not take this in to consideration to offer him a fare well. PHILADELPHIA, HERE I COME! :: English Literature PHILADELPHIA, HERE I COME! A young prospective man called Gar O 'Donnell is the centre point of the book 'Philadelphia Here I Come'. The action takes place the night before and the morning of Gar's departure for Philadelphia. Gar lives in a small village in County Donegal called Ballybeg. Gar finds his home life very boring and repetitive. Through out the book Gar shows his feelings about the village by what he says and does. "Aye, and but for Aunt Lezzy and the grace of God, you'd be there tonight, too, watching the lights go out over the village, and hearing the front doors being bolted, and seeing the blinds being raised; and you stamping your feet to keep the numbness from spreading, not wanting to go home, not yet for another while, wanting to hold on to the night although nothing can happen now, nothing at allà ¢Ã¢â€š ¬Ã‚ ¦". This is one example were Gar shows his realistic views. The book was set in the 1960's, and at this time Ireland was a lot different than it is today. There was a lot of Irish emigrating to nearer countries to live a new life. One reason for this was because the Irish economy was in a depressed state. The people of Ballybeg were slaves of routine, and they had very little to do in such a small community. Gar soon realises that he will never be able to live an exciting life in Ballybeg and soon recognizes that he has no future in his home village. This leads to Gar deciding to move to Philadelphia, where he hopes life has a better impact on his future. There are many reasons for Gar wanting to leave Ballybeg. Gars life has been a very emotional time. Gars mother died shortly after his birth, this was a huge upset for him and his father. To make things worst Gar's father, S.B, does not get on with his only son, even know Gar lives and works with him. They see each other every day and still their communication levels are low. ''If he wants to speak to me he knows where to find me! But I'm damned if I'm going to speak to him first''. This is one example of were Gar gets so annoyed he starts to take it out on poor Madge who is trying to help. Gar doesn't mean to but it is he is so annoyed at the sate of his life. They only communicate when essential. Gar is leaving for Philadelphia in the morning, and still his father does not take this in to consideration to offer him a fare well.

Thomas Hardy Poem Interpretation

Poems for essay: Neutral Tones, A Broken Appointment, The Moth-Signal. Interpretation is said to be an explanation or conceptualization of a work of literature or other art form by a critic. Hardy is known for integrating personal events from his life, into his poems that allow the reader to develop a fully rounded view of what he was trying to convey in his work. Love and its effects are one of his most famous themes that are the basis of many of his poems. Hardy tends to use references to many of his loves in his life in his poems especially his first wife Emma.The context from which he writes helps immensely when deducing the meaning of his works. However, knowledge of the poet’s background is not a necessity when interpreting all poems nor does it always influence the interpretation given by the reader; this only true to a certain extent. In the poems: â€Å"Neutral Tones†, â€Å"A Broken Appointment† and â€Å"The Moth- Signal (Edgon Heath)† are all e xamples of poems by Thomas Hardy that does not require awareness of his background to be interpreted by the reader.The poem, â€Å"Neutral Tones† can be deciphered is about a man who loses his true love and thus skews his view of love forever. The first stanza may be interpreted as the setting of which this heartbreaking moment between these two lovers took place. The setting bares no identification needed towards the writer and can be easily interpreted by the reader. The proceeding stanzas basically describe the scenarios in the relationship that led to ultimately the couple going their separate ways and as a result changes the man’s perception of love as the event is relayed from his point of view.This poem is just based on a love gone wrong and does not need Hardy’s background information to be successfully understood by anyone who reads it. His personal detached tone from the poem allows this to be possible. Along with â€Å"Neutral Tones†, â€Å"A Broken Appointment† follows the same trend of love and freedom to be interpreted without having knowledge of his past loves. This poem is about a man who is now reflecting later about the time he was stood up by the woman he loved. This is an issue that happens regularly and does not need to be referenced to sometime in the author’s life to be analyzed thoroughly.This poem was also written generally so it also bore no semblance to the life of Hardy. This goes to show that the background of an author when interpreting a poem is not utter importance. In addition, â€Å"The Moth-Signal (Edgon Heath)†, is another one of Hardy’s poems that lack the need for the context from which the poet writes. In this poem, there is an affair by a woman that is summoned to her lover via a moth being burned in the flames of a candle to indicate her lover was present.Since infidelity is a common issue, the background of Hardy is not needed to influence the interpretation of th is poem. In all of the above mention poems, they all encompassed a plot that was easily identifiable by any reader. The thread of love and heartbreak ran through each and they are all poems that are relatable to all who reads these poems. This gives proof that a poet’s background does not need to be known in order to interpret a poem nor influence its interpretation.

Axial stresses - Free Essay Example

Sample details Pages: 12 Words: 3697 Downloads: 7 Date added: 2017/06/26 Category Physics Essay Type Descriptive essay Tags: Stress Essay Did you like this example? An analysis of the state of stresses generated by torsion in twisted non-circular bars Abstract One of the main problems that must be solved in the design of the machine components stressed in torsion is to establish their optimum shapes and dimensions in order to resist for a given twisting load. Also, in the case of some parts (crankshafts, ornamental bars, blades of screw propeller for torpedoes) manufactured by using plastic torsion as technologic operation the designer must determine the needed deformation energy. An important factor that has a direct implication on the designing methodology and on the resistance to torsion of these components is the state of stress generated by the twisting load application. Don’t waste time! Our writers will create an original "Axial stresses" essay for you Create order Usually, the components that transmit or must support twisting moments are circular or tubular in cross-section, but in certain cases components with other than circular sections can be used. The present paper reviews the main aspects concerning the state of stress generated by elastic and plastic torsion in non-circular bars. Keywords: Torsion; State of stress; Shearing stresses; Axial stresses; Non-circular bars 1. Introduction By considering a non-circular bar stressed in torsion, the following effects generated by the twisting load application are emphasized by the Theory of Elasticity in the twisted bar: the helical orientation of the initially straight fibres, especially, for large angles of twist; the warping of the plane cross-sections; the change in length of the material fibres and differences in length from a deformed fibre to another; the modification of the initially right angle between the deformed fibre and the section normal to it. One of the main factors that generates or influences these effects is the state of stress, which occurs in bars during torsion. Relating to this state of stress generated by torsion, the Theory of Elasticity and Plasticity discusses, generally, about the shearing stresses that act on the cross-sections of the twisted bars. 1.1. Remark The solutions for the problems concerning the shearing stresses magnitude and distribution on the cross-sections of elastic, elastic-plastic and plastic twisted bars, circular or non-circular in cross-section, can be found in Refs.[1],[2],[5],[6],[8],[9],[10],[11],[12],[13],[14],[15],[16],[17]and[18]. Some authors analyzed the possibility that axial stresses to be developed in certain conditions in the twisted bars. Thus, an experimental analysis concerning the development of axial stresses during hot torsion tests, for the case of round samples twisted for different ranges of temperature, is presented in Ref.[7]. According to the obtained results it has been concluded that hot torsion develop in twisted bars axial stresses whose distribution and magnitude depend on temperature range. Some aspects relating to the generation of axial stresses in the twisted non-circular bars are also discussed in Ref.[3]. The knowledge of the values and distribution of the stresses in a twisted bar is of a great importance for the designing and manufacturing processes of different machine components. Thus, by knowing the maximum value and the distribution of the stresses on different sections, the designer can establish an optimum shape of the component section can determine the optimum dimensions of the machine components and can verify certain sections of the bar stressed by torsion. Also, the knowledge of the stresses value and distribution will permit to determine the deformation energy needed to manufacture different parts by using torsion as technologic operation. On the other hand, the knowledge of the state of stress due to torsion will permit to elucidate different phenomena that occur in the twisted bars. Concerning the state of stress generated by torsion in the twisted non-circular bars, the present paper addresses the following questions: 1. What is the real state of stresses generated by torsion in a non-circular bar? 2. What is the variation of the stresses on the cross and longitudinal sections of the twisted non-circular bars? In answer to these questions, the paper performs an analytical analysis concerning the shearing stresses distribution and, based on some theoretical suppositions or experimental investigations, discusses the possibility that the axial stresses to be generated and developed in the twisted non-circular bars. 2. Shearing stresses distribution on different cross-section shapesa review According to the Theory of Elasticity and Plasticity related to torsion, the state of stress on the cross-section of a twisted bar is characterized by the following general properties[2],[3],[6],[10],[13]and[17]: in the case of elastic torsion, the state of stress in an arbitrary point of the section corresponds to the state of pure shear and the shearing stress vector reaches its maximum value on the section contour; in the case of elastic-plastic torsion, the following two regions can be distinguished on the cross-section of bar: an elastic region, located in the close proximity of the axis of bar, where the Hookes law is valid at any point and the stress distribution presents similar aspects like in the case of elastic torsion; a plastic region, which starts when the shearing stress reaches the yield valuekand satisfies the condition of plasticity expressed by the relation: wherexzandyzare the non-zero components of the shearing stresses resultant andmaxis the maximum value of the shearing stress; in the case of fully plastic torsion, by considering that the whole section is in yielding state, the shearing stress vector is constant in magnitude and its direction is perpendicular to the normal on the contour of the plastic region. The distribution and the magnitude of the shearing stresses present different aspects as a function of cross-section shape and dimensions. This paragraph analyses the main aspects concerning the shearing stress distribution on the most frequently used non-circular sections. 2.1. Sections having curvilinear contours In the case of a solid elliptic cross-section, having the semi-axesaandband stressed by the twisting momentT( 1), the distribution of the shearing stresses presents the following aspects[1],[6],[13],[14]and[15]: the resultant of the shearing stresses can be calculated by using the following relation: the two components of the shearing stress vector (xz,yz) have a linear variation along the Oxand Oyaxis, these components and their maximum values being expressed by the following relations: the maximum stress will occur on the elliptic contour in the point closest by the axis of bar atx=a,y=b, its value being given by the relation: whereis the angle of twist per unit length andGis the transverse modulus of elasticity. From the diagram shown in 1, we can observe that the maximum value of the shearing stress is reached in the pointsBandDwhere it is equals toxz. the components of the shear stress vectorxzandyzare equal to zero on the Oyand Oxaxis, respectively; if we consider the ratio between the two components of the shearing stresses vector we obtain the following relation: this relation expresses the fact that on an arbitrary direction OM the shearing stress vector has a constant direction. Plastic yielding will occur at the extremities of the minor axis of the ellipse whenmax=k, the corresponding twisting moment being equal to: In the case of an elliptic section having an elliptic hole ( 2), the shearing stresses variation presents the same aspects like in the case of the solid elliptic sections[11]. By considering a section having a shape in the form of an inverse ellipse ( 3), the components of the shearing stress vector will be given by the following relations: xz=2GcsinuF1,yz=2GccosuF2, whereF1andF2are functions that depend onkand on the real parametersuandv[11]. In the case of a lobe keyed section ( 4), by using a conformable transformation, the shearing stress components can be obtained from the following relation: zbeing a complex variable[11]. In the case of a section in the form of a curvilinear triangle ( 5), the maximum shearing stress occurs in the point located at the middle of the triangle side and has the following value: max=1.15Ga, abeing the triangle side[2]and[9]. 2.2. Sections having contours formed by straight sides In the case of a section in the form of equilateral triangle, having the heighthand the equations of its sides given by:View the MathML source, the distribution of the shearing stresses on the section shown in 6presents the following aspects[1],[2],[6]and[8]: the stress vector components can be calculated using the following relations: the maximum intensity of the shearing stress vector will be reached at the middle of the triangle sides and it can be determined using the following relation: whereais the size of the triangle side. Yielding will start to set in when the shear stress vector reaches the intensitykand the twisting moment becomes equal to: the fully plastic twisting moment can be calculated using the following relation: In the case of a rectangular cross-section, the distribution of the shearing stresses presents the following particularities[5],[12]and[15]: the maximum shearing stress occurs at the middle of the longest side, its value being given by the relation: wherebandaare the dimensions of the cross-section (bbeing the longer side) andmis a factor given in tables as a function ofbanda; the distribution of the shearing stresses on the cross-section is shown in 7; we can observe that at the middle of the smaller side the shearing stress is equal to: xzmax=yzmax, being a coefficient also given in tables as a function of ratiob/a. for a given twisting moment and cross-section area, the maximum shearing stress reaches its smallest value in the case of dimensions leading to the smallest polar second moment of area; for a narrow rectangular cross-section[8],[10]and[18], according to equationxz=2Gx, the shearing stress is linear inx; its maximum value occurs at a/2 ( 8) and is given by the relation: yielding starts at the midpoint of the longer sides when the applied twisting moment becomes equal to: the fully plastic twisting moment is given by the following formula: In the case of a square cross-section[1],[8]and[10], by using a harmonic stress function, the maximum shearing stress will be given by the following relation: abeing the square side andAan expression equal to the yielding starts at the midpoint of the square sides when the stress vector reaches the intensityk; in the case of fully plastic torsion, the twisting moment can be calculated using the following relation: 3. Aspects concerning the possibility that axial stress to be generated by torsion Let us consider the particular case of a rectangular bar stressed in torsion by applying the twisting moment at its both ends. After the twisting load application, we can observe the following effects generated by torsion in the twisted bar: the main effect of the twisting load application will be the helical orientation of the initially straight longitudinal edges of bar ( 9a) and hence the change of their length[4]. Thus, by examining the half of a longitudinal section of bar as non-deformed ( 9b) and deformed after its twisting ( 9c) we can remark the following aspects: the initially straight edge AA of the rectangle OAAO will occupy the new position AA, after its helical orientation around a cylindrical surface of radiusR=OA=OA; the helical orientation of the edge AA will determine the modification of its length from the initial valueL0=LAAto the valueLAA=LAA+LA, where LAis the elongation of the edge of bar; the value of the elongation can be calculated using the following formula: whereRis the radius of the cylindrical surface described by the points of edge during torsion,L0the initially length of edge andnis the number of complete rotations of the ends of bar. 3.1. Remark From relation(21), we can observe that the elongation and the changes in length of the edge depend on the applied angle of twist, the position of the edge in comparison with the neutral axis of bar and the dimensions of bar. in the frame of the same rectangle OAAO, we consider now the side MM which after its twisting will become the helix MM folded around a cylindrical surface of radius OM=OM. From the evident inequality OMOA, we can conclude that the length of the helix MM is smaller than the length of the helix AA (LAALMM). Hence, it results that the changes in length of the rectangle sides or edges of bar depend on their position in comparison with the neutral axis of bar. By this point of view, we can divide the longitudinal section of bar in the following two regions as deformed after twisting: the region from the neutral axis and its neighbouring, where the elongation of the rectangle sides presents the smallest values and becomes equal to zero for the neutral axis; the region from the periphery of section, where the elongation of the rectangle sides presents the greatest values. Hence, we can suppose that the region from the neutral axis of bar, where are registered the smallest deformations, will oppose to the tendency manifested by the peripheral region to be elongated under the action of the twisting load. By examining the internal macrostructure on the etched longitudinal section of a square bar, made in low carbon steel and cold twisted with an angle of twist per unit length equal to 9.42102radmm1( 10), we can observe the presence of two distinct regions as deformed in the axial direction. The first region is located in the close proximity of the axis of bar and represents the rolling core, initially present in the non-twisted bar. In this region, the material will oppose to the tendency of bar to be deformed under the action of the twisting moment and hence minimum torsional deformations and the tendency to contract the material fibres will be registered. The second region is located in the peripheral zones of bar, where maximum torsional deformations and considerable elongation of the material fibres will take place. The above-presented aspects are confirmed by analyzing the variation of the material hardness determined in these two regions after one complete revolution of the ends of bar; thus: in the region from the neutral axis of bar, the hardness increases from a value equal to 196 HB before twisting till a value equal to 212 HB after twisting; in the region from the periphery of bar, the hardness increases from the value equal to 207 HB before twisting till a value equal to 230 HB after twisting. The differences between the values of the material hardness from the periphery and the neutral axis of bar can confirm the presence of these two distinct regions as deformed in the axial direction after twisting. Let us now consider two longitudinal edges of the same outer face of a rectangular bar, the first AA that represents the edge of bar and the second NN placed at the middle of the face ( 11). We can remark that, because these edges will be folded during torsion around cylindrical surfaces of different radii (OA and ON, respectively), the resulted helixes will present different lengths (LNNLAA). The above-presented aspects concerning the effects of torsion in the axial direction of non-circular bars can lead to the following conclusions: The modification of the length of bar edges during torsion and the differences in length resulted between the generated helixes indicate and determine the development of axial deformations and stresses in the twisted non-circular bars. 3.2. Remark The aspects relating to the generation and distribution of the axial stresses in the round bars twisted over the yield limit of material are analyzed in[7]. The analysis proves that the axial stresses can be tensile or compressive depending on temperature and material properties. The main cause that determines the appearance of the compressive stresses is attributed to grains deformation, which has a maximum intensity at low temperatures and at the beginning of the deforming process. The slipping of the grains, which has a maximum intensity at high temperatures and at the end of the deforming process is considered the cause that determines the appearance of the tensile stresses. The opposite tendencies manifested between the outer and inner regions of a non-circular bar indicate the generation of two opposite axial stresses in these two regions: tensile in the peripheral region and compressive in the region from the neutral axis. The differences in length resulted between the deformed longitudinal edges from the outer surface of bar and the variation of their elongation as a function of their position in comparison with the neutral axis of bar can explain the warping of the non-circular sections. These differences can, also, indicate the possibility that the distribution of the axial deformations and stresses to become non-uniform on the longitudinal sections of the twisted non-circular bars. 4. Discussion The distribution of the shearing stresses on the cross-section of the twisted bars is imperative to be known because: the values of these stresses are used in design to determine the shape and dimensions of the section of bar; the shearing stresses distribution and value have an important contribution and influence on different phenomena that occur in bar during torsion. The main aspects concerning the shearing stress variation emphasized by the above-presented analysis are as follows: on the cross-section of twisted non-circular bars only shearing stresses will occur and act; these stresses will determine a state of pure shear. the variation of the shearing stresses depends, generally, on the cross-section shape; thus: in the case of an elliptic section, the shearing stresses resultant has a constant direction that is parallel to the direction of the tangent to the boundary where it is cited by the considered radius; in the points of a given diameter the stresses resultant has a linear increase as we move away from its origin. in the case of rectangular, square and triangular sections the variation of the shearing stresses is non-linear on all the directions and depends on the section shape and dimensions. the shearing stress vector attains its maximum value on the contour of cross-section indifferently of its shape; the maximum intensity of the shearing stress vector will be reached in different points of the contour as a function of cross-section shape and dimensions; thus: in the case of an elliptic section, the maximum shearing stress will occurs at the extremities of the minor axis of the ellipse; in the case of a rectangular bar the maximum shearing stress is reached at the midpoints of the longest sides; in the case of an equilateral triangle the maximum shearing stress will occur at the midpoints of the triangle sides. Generally, the shearing stress decrease in the sense of displacement from the outer contour of cross-section to neutral axis and reach the zero value in the point located on the neutral axis. But, as a function of cross-section shape, the zero value of the shearing stress can be also reached and in other points of the cross-section. Let us consider the corner of a rectangular bar ( 12) and an element of area located in the close proximity of this corner. We can observe that, because on the lateral surface of bar the stress componentsxy=zy=0 are equal to zero, the shearing stress componentsxz,yzwill be, also, equal to zero. Hence, we can conclude that, for a polygonal section, the shearing stresses are equal to zero in the close proximity of the corners. From the above-mentioned effect of torsion concerning the modification of the angle between the longitudinal edge and the cross-section edges of a rectangular bar (initially right angles), we can remark the following aspects: the modification of this angle is smaller in the close proximity of the bar edge and greater near the longitudinal axis of the bar face, and, hence, the modification of the cross-section contour will take place. by examining the internal macrostructure of the material on an etched square cross-section ( 14), we can distinguish two regions as deformed in the transverse plane: the first region is located in the close proximity of the axis of bar and represents the rolling core, initially present in the non-twisted bar; the second region is located in the peripheral zones of bar. The irregular shapes of these regions point out that for large angles of twist the deformation on the cross-section can become non-uniform. By taking into account these aspects concerning the non-uniform deformation of cross-section, we can conclude that, in certain conditions, the shearing stresses can become non-uniform distributed on the cross-section of the twisted non-circular bars. The axial stresses can occur during torsion of the non-circular bars and can be generated by the modification in length of the longitudinal sections. These stresses can be tensile or compressive as a function of position of the longitudinal section in comparison with the neutral axis of bar. Thus, on the peripheral sections of bar the tensile stresses will occur and on the inner sections the compressive stresses will act. In certain conditions, the axial stresses can present a non-uniform distribution on the same longitudinal section or between different sections of bar as a function of their position in comparison with the neutral axis. 5. Conclusions The general theory of elastic or plastic torsion, when discusses about the state of stresses generated by torsion in the twisted bar, take only into consideration the shearing stresses that occur on the cross-section. According to the above presented aspects and suppositions, the complete state of stresses generated by torsion in the twisted non-circular bars must consider not only the shearing stresses on the cross-sections but also axial stresses, compressive or tensile, on the longitudinal ones. The development of axial stresses (tensile or compressive) in the twisted non-circular bars can explain the changes in the length (elongations or contractions) that take place during torsion in the case of bars unconstrained from the axial displacement. Hence, the knowledge of the distribution and values of axial stresses that occur during torsion will permit to determine the precise length of the semi-parts used to manufacture different mechanical components using torsion as technologic operation.